JP2008062024A - Heating dehumidifier - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an efficient heating dehumidifier having less noise. <P>SOLUTION: The heating humidifier 400 comprises a warm air channel part 241; a wet air channel part 242; a high-temperature side heat exchange part 420 for heating the gas flowing through the warm air channel part 241; a low-temperature side heat exchange part 430 for cooling the gas flowing through the wet air channel part 242; and a Stirling engine 410 including a heat generating head 411 and a heat absorbing head 412. The high-temperature side heat exchange part 420 performs heat exchange so that the gas is heated by the heat generating head 411 of the Stirling engine 410, and the low-temperature side heat exchange part 430 performs heat exchange to cool the gas by the heat absorbing head 412 of the Stirling engine 410. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a heat dehumidifier.

  In recent years, there has been an increasing demand for washing and drying machines for washing clothes and the like from washing to drying. In particular, if you want to dry a small amount of laundry immediately, reduce the time to dry outdoors or indoors, or if you cannot wash during the day, you can wash your clothes at night and dry it after dehydration. Therefore, convenience according to the lifestyle of the user is evaluated.

  In such a heating and dehumidifying apparatus such as a laundry dryer, a conventionally used drying method of laundry is generally heating an electric heater or gas while rotating a rotating tub containing a laundry containing moisture. Drying is performed by supplying warm air heated by means. For example, in the water-cooled dehumidifying drier described in JP-A-63-122500 (Patent Document 1), hot and humid air during and / or after drying is directly discharged outside the apparatus, Alternatively, reflux circulation is performed in which air is cooled by a cooling and dehumidifying means such as air or tap water outside the apparatus, or after being cooled by water and subjected to heat exchange and dehumidification, and then returned to the heating means.

  In general, in order to shorten the drying time of the laundry, for example, it is conceivable to increase the heat capacity of a heating means such as a heater, but the power consumption increases proportionally.

  Further, when heat exchange dehumidification with cooling water is used, a large amount of water is used, and the amount of water consumption increases in proportion to the drying time.

  Therefore, for example, in Japanese Patent Laid-Open No. 60-220097 (Patent Document 2), in order to reduce the power consumption and the amount of water used, a condenser ( A drying method has also been proposed in which an evaporator (corresponding to the cooling and dehumidifying means described above) and an evaporator (corresponding to the cooling and dehumidifying means described above) are provided to effectively use heat and cold. According to this drying method using a heat pump, air can be heated and cooled and dehumidified without using a heater or water, so that power consumption can be reduced and water can be saved.

  Japanese Patent Application Laid-Open No. 2004-215543 (Patent Document 3) and Japanese Patent Application Laid-Open No. 2005-40316 (Patent Document 4) circulate by exhausting circulating air in an air circulation path used for drying clothes. A clothes dryer and a dryer with a washing function using a heat pump are described which prevent the amount of heat of air from increasing and stabilize in a safe state.

  Japanese Patent Laying-Open No. 2006-212117 (Patent Document 5) describes a clothes drying apparatus that continues the operation of a compressor when a drying operation is interrupted in a clothes dryer using a heat pump. Japanese Patent Laying-Open No. 2006-61353 (Patent Document 6) describes a clothes drying apparatus using a heat pump that stops the operation of the compressor for a predetermined time after the drying operation is interrupted. Has been. By doing in this way, when the drying operation and the interruption of the drying operation are repeated in a short time, the burden on the compressor is reduced, and the return of the hot air temperature by the heat pump device is accelerated.

In Japanese Patent Application Laid-Open No. 2006-272024 (Patent Document 7) and Japanese Patent Application Laid-Open No. 2005-261703 (Patent Document 8), before starting the drying process, the operation of the compressor is started in advance and the drying process is started. A washing and drying machine using a heat pump is described which reduces the time.
JP 63-122500 A Japanese Unexamined Patent Publication No. 60-220097 JP-A-2004-215543 JP 2005-40316 A JP 2006-212117 A JP 2006-61353 A JP 2006-272024 A JP 2005-261703 A

  However, even with a drying method using a heat pump, since a compression means such as a compressor is newly used to compress the refrigerant, there is a problem that noise and vibration are generated during operation and noise during drying is increased. In addition, depending on the type of refrigerant used in the compressor, there arises a problem that the cost after disposal is high. In addition, from the perspective of preventing global warming, it is increasingly necessary to reduce the power consumption of electrical products in the future, and dryers and washing dryers are required to improve drying functions and reduce power consumption. .

  In addition, when a heat pump is used in the dryer, the amount of heat of the circulating air is increased by driving the heat pump, the temperature of the refrigerant of the heat pump is increased, and the temperature of the refrigerant is increased and the pressure is increased. Although it is possible to control the output of the heat pump by inverter control or the like, it is extremely difficult to significantly reduce the output, and it is difficult to reduce the amount of heat applied even when the amount of heat of the circulating air is excessive. Moreover, in order to compress and liquefy the high temperature and high pressure refrigerant | coolant, the burden concerning a heat pump becomes large. Therefore, the dryers described in Japanese Patent Application Laid-Open No. 2004-215543 (Patent Document 3) and Japanese Patent Application Laid-Open No. 2005-40316 (Patent Document 4) exhaust the circulated air whose amount of heat has increased to the outside. Unnecessary heat generated by the heat pump or steam contained in the circulating air may be discharged into the room where the dryer is installed, resulting in an increase in the amount of heat in the whole room or condensation due to the discharged steam. is there.

  In clothes dryers that use heat pumps, it takes a certain amount of time for the refrigerant pressure in the piping to reach an equilibrium state when the drying operation is interrupted and for the refrigerant to vaporize and liquefy when the drying operation is resumed. . Therefore, when the drying operation is resumed in a short time after the interruption of the drying operation, the drying operation is interrupted as in the clothes dryer described in JP 2006-212117 A (Patent Document 5). Nevertheless, it is necessary to continue driving the compressor, which consumes unnecessary power and places a heavy burden on the compressor. On the other hand, when the drying operation is interrupted as in the clothes dryer described in Japanese Patent Application Laid-Open No. 2006-61353 (Patent Document 6), if the compressor is not operated thereafter for a certain period of time, the drying operation is performed. The drying operation cannot be resumed in a short time after the interruption.

  Moreover, like the washing dryer described in JP 2006-272024 A (Patent Document 7) and JP 2005-261703 A (Patent Document 8), the compressor is operated in advance before entering the drying process. This causes unnecessary heat and noise, and increases the power consumption.

  Accordingly, an object of the present invention is to provide an efficient heating and dehumidifying device with less noise.

  A heating and dehumidifying device according to the present invention includes a first air path and a second air path for circulating gas, and a first heat exchange unit for heating the gas flowing through the first air path. A second heat exchanging part for cooling the gas flowing through the second air passage, and a Stirling engine including a heat generating head and an endothermic head, the first heat exchanging part being a heat generating head of the Stirling engine The heat exchange is performed so as to heat the gas, and the second heat exchange unit performs the heat exchange so that the gas is cooled by the heat absorption head of the Stirling engine.

  Conventionally, in a heat pump used in a heat dehumidifying apparatus, heat exchange is performed between a condensing unit that compresses a refrigerant by a compressor to change from gas to liquid and an evaporation unit that expands the refrigerant to change from liquid to gas. ing. That is, in the heat pump, the refrigerant moves from the condensing unit through the pipe or the like to the evaporating unit, changes from liquid to gas, and moves from the evaporating unit through the pipe or the like to the condensing unit to change from gas to liquid. It is necessary to repeat changing.

  On the other hand, the Stirling engine reciprocates the displacer in the cylinder, thereby compressing the working gas such as helium in the compression space to heat the heat generating head and expand the heat generating head to cool the heat absorbing head. As described above, in the Stirling engine, the working gas remains in a gaseous state and moves only between the compression space and the expansion space. The compression space and the expansion space are disposed at both ends of one cylinder, for example. In this case, the working gas reciprocates from one end of the cylinder to the other end while maintaining the gaseous state. .

  As described above, in the Stirling engine, the moving distance of the working gas is short, and it is not necessary to change the state of the refrigerant between the gas and the liquid. Therefore, the responsiveness of the Stirling engine is higher than that of the heat pump. For example, the time required from the start of driving the Stirling engine until the heat generating head and the heat absorbing head reach a predetermined temperature, the evaporation unit and the condensing unit are set to a predetermined temperature after starting the heat pump. It is shorter than the time required to become.

  Therefore, by using a Stirling engine, it is not necessary to start up for a long time before the start of the drying operation or at the start of the drying operation. Therefore, the controllability is higher than that of the heat pump, and energy saving, that is, energy consumption is effectively reduced. Thus, it is possible to obtain a heating and dehumidifying device that facilitates energy saving. As described above, the heating and dehumidifying device including the Stirling engine can shorten the time required to start the heating and dehumidifying device, and is required when the operation is once interrupted and then restarted during the operation of the heating and dehumidifying device. Time can be shortened.

  Further, the vibration system of the heat pump used in the conventional heat dehumidifying apparatus is a complicated vibration system including rotation vibration because a compressor is used for compression and expansion of the refrigerant. On the other hand, a Stirling engine has a simple vibration system compared to a heat pump. That is, in the Stirling engine, only a linear motion of reciprocation of the displacer is performed.

  Thus, since the Stirling engine has a simple vibration system, it is easy to absorb vibration. For example, the vibration can be easily suppressed by providing a vibration absorbing member such as a spring having the co-frequency of the displacer as the natural frequency. In a Stirling engine, vibration can be easily suppressed, so that noise due to vibration is less likely to occur.

  In this way, vibration and noise can be reduced, and usability, ie easy to use, energy saving, ie consumption, does not deteriorate the indoor environment where the dryer is installed. It is possible to provide a heating and dehumidifying device that can effectively reduce energy and facilitate energy saving.

  The heating and dehumidifying device according to the present invention includes a circulation path for allowing gas to flow from the second air path into the first air path, and the gas in the second air path is in the second heat exchange section. It is preferably cooled, flows into the first air passage through the circulation path, and is heated in the first heat exchange section.

  Thus, the gas that has flowed into the second air passage is cooled in the second heat exchange section, flows into the first air passage through the circulation path, and is heated in the first heat exchange section. Therefore, it can dehumidify efficiently.

  In the heating and dehumidifying apparatus according to the present invention, it is preferable that the heat generating head is disposed in the first air path to constitute the first heat exchange unit.

  This eliminates the need for a heat transfer path between the heat generating head and the first heat exchanging section, and wastes heat in the path between the heat generating head and the first heat exchanging section. Can be prevented.

  In the heating and dehumidifying device according to the present invention, it is preferable that the first heat exchange unit includes a fin disposed so as to contact the heat generating head.

  By doing in this way, gas can be efficiently heat-exchanged in a fin. In addition, the heat dehumidifying device can be reduced in size.

  In the heating and dehumidifying device according to the present invention, the first heat exchanging unit includes a heating unit for heating the gas and a heat conduction medium through which a heat conduction medium for conducting the heat of the heating head to the heating unit flows. It is preferable to have a flow path.

  By doing in this way, it becomes easy to optimize the position and shape of a 1st heat exchange part according to the shape of an air path, etc.

  In the heating and dehumidifying apparatus according to the present invention, it is preferable that the heat absorbing head is disposed in the second air passage to constitute the second heat exchange unit.

  This eliminates the need for a path for transmitting cold air between the heat absorbing head and the second heat exchange unit, and wastes cold air in the path between the heat absorbing head and the second heat exchange unit. Can be prevented.

  In the heating and dehumidifying device according to the present invention, it is preferable that the second heat exchange part includes a fin disposed so as to contact the heat absorbing head.

  By doing in this way, gas can be efficiently heat-exchanged in a fin. In addition, the heat dehumidifying device can be reduced in size.

  In the heating and dehumidifying device according to the present invention, the second heat exchanging unit includes a cooling unit for cooling the gas and a heat transfer medium through which a heat transfer medium for transferring the heat of the cooling head to the cooling unit flows. It is preferable to have a flow path.

  By doing in this way, it becomes easy to optimize the position and shape of a 2nd heat exchange part according to the shape of an air path, etc.

  The heating and dehumidifying device according to the present invention includes a connecting pipe disposed between the heat generating head and the heat absorbing head, and the heat generating head is disposed in the first air passage to constitute the first heat exchange unit. The heat absorbing head is disposed in the second air passage to form a second heat exchange unit, and a connection pipe is provided between the heat generating head and the heat absorbing head, and is connected to the heat generating head and the heat absorbing head. The pipes are arranged coaxially, and it is preferable to arrange the heat generating head, the heat absorbing head, and the connecting pipe in the circulation path.

  By doing so, the circulation path can be shortened to suppress the pressure deficit, and the thermal influence between the heat generating head and the heat absorbing head can be reduced by the air layer around the connecting pipe.

  As described above, according to the present invention, it is possible to provide an efficient heating and dehumidifying device with less noise.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(Embodiment 1-1)
FIG. 1 is a perspective view schematically showing the overall appearance of a washing / drying machine provided with the heating / dehumidifying device of the present invention as Embodiment 1-1 of this invention, and FIG. 2 is a washing / drying machine of FIG. It is a sectional side view which shows roughly the cross section which looked at the II-II line | wire direction.

  As shown in FIGS. 1 and 2, the washing and drying machine 200 includes a main body 210, a water tank 220 attached to the inside of the main body 210, and a water tank 220 as a container for storing laundry as an object to be dried. And a rotating drum 230 supported rotatably inside.

  An outer door 201 is attached to the front surface of the main body 210. An inner door 203 is attached inside the outer door 201. By opening the outer door 201 and opening the inner door 203, the laundry can be put into or taken out of the rotating drum 230 through the laundry inserting port 202 provided on the front surface of the main body 210. The laundry input port 202 can be closed by closing and closing the outer door 201. The inner door 203 has a central portion made of transparent glass so that the inside of the rotary drum 230 can be visually recognized, and has a recessed bowl shape, a so-called basin shape. A door packing 204 made of an elastic material such as rubber is fitted and fixed to the peripheral wall of the water tub 220 on the laundry input port 202 side. When the inner door 203 is closed, the door packing 204 is in close contact with the peripheral edge of the inner door 203 so that the water tank 220 is sealed.

  The rotating drum 230 is supported so as to rotate around the shaft portion 231 inside the water tank 220. In this way, the drum type washing and drying machine 200 has a double structure composed of the water tank 220 and the rotating drum 230. The rotary drum 230 includes a drum body 232 that forms an inner peripheral wall surface at the center in the rotation axis direction, a drum lid 233 that forms an opening at one end, and a drum bottom 234 that forms an inner bottom wall surface at the other end. Are generally made from stainless steel sheet. An uneven surface such as a rib is formed on the drum bottom 234 by pressing to attach a structural component such as the shaft portion 231 and support a desired load, thereby improving the strength of the bottom wall surface. A large number of small holes 235 for water supply, drainage, and ventilation are provided in the peripheral wall and bottom of the rotary drum 230. A fluid balancer 205 is fixed to the outer peripheral edge of the drum lid 233 to prevent vibration during rotation. The shaft portion 231 includes a shaft of a drum rotation drive motor 236 for rotating the rotary drum 230. The rotation of the drum rotation drive motor 236 is controlled by an inverter circuit. The water tank 220 is elastically supported by a coil spring (not shown) from the upper part and by an anti-vibration damper (not shown) from the lower part. A water supply path 205 connected to tap water is disposed above the water tank 220, and is connected to the water tank 220 via a detergent charging unit 207. A water supply valve 208 is provided in the middle of the water supply path 205, and supply from the tap water to the water tank 220 is controlled by opening and closing the water supply valve 208. A drain valve 206 is provided at the bottom of the water tank 220, and washing liquid and the like can be drained from the water tank 220 to the outside of the main body 210 by opening and closing the drain valve 206.

  FIG. 3 is a cross-sectional view showing the entire cross section of the Stirling engine.

  As shown in FIG. 3, the cylinders 110 and 111 are central to the assembly of the Stirling engine 100. The axes of the cylinders 110 and 111 are aligned on the same line. A piston 112 is inserted into the cylinder 110, and a displacer 113 is inserted into the cylinder 111. The piston 112 and the displacer 113 reciprocate without contacting the inner surfaces of the cylinders 110 and 111 by the gas bearing mechanism during operation of the Stirling engine 100. The piston 112 and the displacer 113 move with a predetermined phase difference.

  A cup-shaped magnet holder 114 is provided at one end of the piston 112. A displacer rod 115 projects from one end of the displacer 113. The displacer rod 115 passes through the piston 112 and the magnet holder 114 so as to freely slide in the axial direction.

  The cylinder 110 holds the linear motor 120 outside the portion corresponding to the operation area of the piston 112. The linear motor 120 includes an outer yoke 122 having a coil 121, an inner yoke 123 provided so as to be in contact with the outer peripheral surface of the cylinder 110, and a ring shape inserted into an annular space between the outer yoke 122 and the inner yoke 123. Magnet 124 and synthetic resin end brackets 125 and 126 for holding the outer yoke 122 and the inner yoke 123 in a predetermined positional relationship. The magnet 124 is fixed to the magnet holder 114.

  The central portion of the spring 130 is fixed to the hub portion of the magnet holder 114. The center portion of the spring 131 is fixed to the displacer rod 115. The outer peripheral portions of the springs 130 and 131 are fixed to the end bracket 126. A spacer 132 is disposed between the outer peripheries of the springs 130 and 131, whereby the springs 130 and 131 maintain a certain distance. The springs 130 and 131 are obtained by making a spiral cut into a disk-shaped material, and cause the displacer 113 to resonate with a predetermined phase difference (ideally about 90 ° phase difference) with respect to the piston 112. Play a role.

  A heat generating head 140 and a heat absorbing head 141 are arranged outside the portion of the cylinder 111 that corresponds to the operating region of the displacer 113. The heat generating head 140 has a ring shape and the heat absorbing head 141 has a cap shape, both of which are made of a metal having good heat conductivity such as copper or a copper alloy. The heat generating head 140 and the heat absorbing head 141 are supported outside the cylinder 111 with ring-shaped internal heat exchangers 142 and 143 interposed therebetween. Each of the internal heat exchangers 142 and 143 has air permeability, and transmits heat of the working gas passing through the inside to the heat generating head 140 and the heat absorbing head 141.

  A space surrounded by the heat generating head 140, the cylinders 110 and 111, the piston 112, the displacer 113, and the internal heat exchanger 142 becomes a compression space 145. A space surrounded by the heat absorbing head 141, the cylinder 111, the displacer 113, and the internal heat exchanger 143 becomes an expansion space 146.

  A regenerator 147 is disposed between the internal heat exchangers 142 and 143. The regenerator 147 is obtained by winding a resin film into a cylindrical shape, and a plurality of minute protrusions are scattered on one side of the film to form a gap corresponding to the height of the protrusion between the films. It is said. A regenerator tube 148 wraps the outside of the regenerator 147 and forms an airtight passage between the heat generating head 140 and the heat absorbing head 141. The heat generating head 140, the regenerator tube 148, and the heat absorbing head 141 are arranged coaxially. The regenerator tube 148 is an example of a connecting tube.

  A cylindrical pressure vessel 150 wraps the linear motor 120, the cylinder 110, and the piston 112. The inside of the pressure vessel 150 becomes a back pressure space 151. On the peripheral surface of the pressure vessel 150, a terminal portion 152 for supplying electric power to the linear motor 120 and a pipe 153 for enclosing a working gas therein are arranged.

  A dynamic vibration absorber 160 is attached to the outer surface of the pressure vessel 150. The dynamic vibration absorber 160 includes a shaft 161 protruding from the center of the end surface of the body portion 150, a plate-like spring 162 fixed at the center to the shaft 161, and a mass (mass) 163 disposed on the periphery of the spring 162. The spring 162 is a stack of a plurality of thin plate springs.

  The Stirling engine 100 operates as follows. A magnetic field penetrating the magnet 124 is generated between the outer yoke 122 and the inner yoke 123 that supply an alternating current to the coil 121 of the linear motor 120, and the magnet 124 reciprocates in the axial direction. By supplying power with a frequency that matches the resonance frequency determined by the total mass of the piston system (piston 112, magnet holder 114, magnet 124, and spring 130) and the spring constant of the spring 130, the piston system has a smooth sine. Start wavy reciprocating motion.

  In the displacer system (the displacer 113, the displacer rod 115, and the spring 131), the resonance frequency determined by the total mass and the spring constant of the spring 131 is set to match the driving frequency of the piston 112.

  By the reciprocating motion of the piston 112, compression and expansion are repeated in the compression space 145. As the pressure changes, the displacer 113 also reciprocates. At this time, there is a phase difference between the displacer 113 and the piston 112 due to flow resistance between the compression space 145 and the expansion space 146. In this way, the displacer 113 having a free piston structure reciprocates in synchronization with the piston 112 with a predetermined phase difference.

  With the above operation, a Stirling cycle is formed between the compression space 145 and the expansion space 146. In the compression space 145, the temperature of the working gas increases based on the isothermal compression change, and in the expansion space 146, the temperature of the working gas decreases based on the isothermal expansion change. For this reason, the temperature of the compression space 145 rises and the temperature of the expansion space 146 falls.

  The working gas that moves back and forth between the compression space 145 and the expansion space 146 during operation passes through the internal heat exchangers 142 and 143 to transmit the heat it has to the heating head 140 and the heat absorption head 141. Since the working gas flowing from the compression space 145 into the regenerator 147 has a high temperature, the heat generating head 140 is heated. Since the working gas flowing from the expansion space 146 into the regenerator 147 has a low temperature, the heat absorbing head 141 is cooled.

  The regenerator 147 functions to pass only the working gas without transferring the heat of the compression space 145 and the expansion space 146 to the space on the other side. The hot working gas that has entered the regenerator 147 from the compression space 145 through the internal heat exchanger 142 gives the heat to the regenerator 147 when passing through the regenerator 147, and enters the expansion space 146 when the temperature is lowered. Inflow. The low-temperature working gas that has entered the regenerator 147 from the expansion space 146 through the internal heat exchanger 143 recovers heat from the regenerator 147 when passing through the regenerator 147, and enters the compression space 145 in a state where the temperature has risen. Inflow. That is, the regenerator 147 serves as a heat storage means.

  When the piston 112 and the displacer 113 reciprocate, vibration occurs in the Stirling engine 100, and the dynamic vibration absorber 160 suppresses this vibration.

  FIG. 4 is a perspective view showing the entire body of the heat dehumidifying apparatus.

  As shown in FIG. 4, the main body of the heating and dehumidifying apparatus 400 includes a Stirling engine 410, a high-temperature side heat exchange unit 420 as a first heat exchange unit, and a low-temperature side heat exchange unit 430 as a second heat exchange unit. Prepare. The Stirling engine 410 includes a heat generating head 411 and a heat absorbing head 412. The configuration and operation of the Stirling engine 410 are the same as those of the Stirling engine 100 shown in FIG. The high temperature side heat exchange unit 420 includes heating fins 421 connected to the heat generating head 411 as fins, and the low temperature side heat exchange unit 430 includes cooling fins 431 connected to the heat absorbing head 412 as fins. The heating fins 421 and the cooling fins 431 have a disk shape, and the central portions are directly connected to the heat generating head 411 and the heat absorbing head 412, respectively. The cooling fins 431, the heating fins 421, and the Stirling engine 410 are arranged so as to be aligned substantially in a straight line, and are integrated to constitute the main body of the heating and dehumidifying device 400. The heating and dehumidifying device 400 includes this main body, a warm air side path portion and a humid air side path portion shown in FIG.

  As described above, in the heat dehumidifying apparatus 400, the high temperature side heat exchanging unit 420 includes the heating fins 421 disposed so as to be in contact with the heat generating head 411, and the low temperature side heat exchanging unit 430 is in contact with the heat absorbing head 412. Cooling fins 431 arranged as described above.

  By doing in this way, heat can be efficiently exchanged between the gas in the heating fins 421 and the cooling fins 431. Moreover, the heat dehumidifying apparatus 400 can be reduced in size.

  FIG. 5 is a cross-sectional view showing an outline when the washing / drying machine is viewed from the direction of the line V-V in FIG. 2.

  As shown in FIGS. 2 and 5, in the main body 210 of the washing / drying machine 200, a hot air path portion 241 and a wet air path portion 242 are arranged on the back side of the rotary drum 230. The hot air path portion 241 and the wet air path portion 242 communicate with the inside of the water tank 220 through an intake port 245 and an exhaust port 246, respectively. The hot air path portion 241 and the wet air path portion 242 are connected via a circulation path portion 243 extending substantially linearly below the water tank 220. The main body of the heating / dehumidifying device 400 is provided in the circulation path part 243 such that the cooling fins 431 are on the wet air path part 242 side and the heating fins 421 are on the hot air path part 241 side. Below the water tank 220, a blower mechanism unit 244 is disposed inside the wet air passage unit 242.

  As shown in FIG. 2, a hot water path portion 247 in the water tank is provided between the inner peripheral wall surface of the water tank 220 and the outer peripheral wall surface of the drum body 232 of the rotating drum 230. Further, the inner peripheral wall surface of the water tank 220, the drum body 232 and the drum bottom 234 of the rotating drum 230 form a water tank inside humid air passage portion 248. An intake port and an exhaust port are provided below the water tank 220. In addition, an exhaust port and an intake port may be provided in a front part, a side surface, or an upper part. As shown in FIG. 5, the exhaust port is connected to the circulation path part 243 via a wet air path part 242 provided outside the back surface of the water tank 220. A blower mechanism unit is disposed in the wet air path unit 242. A main body of the heating and dehumidifying device 400 including a Stirling engine is disposed in the circulation path portion 243 extending substantially linearly. More specifically, the heat generating head 411, the cooling head 412, and the regenerator tube 148 of the main body of the heating and dehumidifying device 400 are disposed in the circulation path portion 243. The circulation path part 243 is connected to the intake port via a hot air path part 241 provided outside the back surface of the water tank 220. The arrow of the dashed-two dotted line in FIG. 2 shows the direction through which a wind flows. In addition, the path | route to the high temperature side heat exchange part 420 of the warm air path | route part 247, the warm air path | route part 241, and the circulation path | route part 243 in a water tank is an example of a 1st air path, the wet air path | route part 248 in a water tank, a humid air path | route The path to the low temperature side heat exchange unit 430 of the part 242 and the circulation path unit 243 is an example of a second air path, the path to the high temperature side heat exchange unit 420 of the circulation path unit 243 and the path to the low temperature side heat exchange unit 430 The path between is an example of a circulation path.

  Hereinafter, the washing process, the rinsing process, the dehydrating process, and the drying process performed using the washing / drying machine 200 configured as described above will be described in the order of steps.

  First, the outer door 201 and the inner door 203 are opened, and after the laundry is loaded from the laundry loading port 202, the inner door 203 and the outer door 201 are closed. Put the detergent in the detergent case and operate the operation panel. Thereby, the outer door 201 and the inner door 203 are locked, the water supply valve 208 is opened, and water is supplied to the water tank 220 through the water supply path 205 and the detergent case 207. When a water level sensor (not shown) detects that the water level in the water tank 220 has reached a predetermined value, the water supply valve 208 is closed, and the rotating drum 230 is rotated by the drum rotation drive motor 236 according to the rotation chart for the washing process. Is done. In this way, the washing process is started.

  In addition, regarding the rotation chart of the rotating drum 230, the rotation speed, the rotation cycle, the reversal cycle, and the like are different for each of the washing process, the rinsing process, the dehydration process, and the drying process, or depending on the type and course of the laundry. The rotation chart is preset. The rotation chart is selected by the user or programmed to be selected automatically.

    When the washing process is finished, the drain valve 206 is opened and the washing liquid is discharged out of the main body. When the drainage is completed, an intermediate dewatering process is performed in which the rotary drum 230 is rotated at a high speed on the rotation chart for the intermediate dewatering process. In the intermediate dehydration process, the washing liquid contained in the laundry is discharged to the inner wall surface of the water tank 220 through the small holes 235 provided in the peripheral wall of the rotating drum 230 by the centrifugal force generated by the high-speed rotation of the rotating drum 230. The washing liquid flows down along the inner wall surface of the water tank 220 and is discharged out of the main body through the drain valve 206.

  When the intermediate dehydration process is completed, the program proceeds to the rinsing process. After the drain valve 206 is closed, the water supply valve 208 is opened, and water is supplied to the water tank 220 through the detergent case. When a water level sensor (not shown) detects that the water level in the water tank 220 has reached a predetermined value, the water supply valve 208 is closed and the rotating drum 230 is rotated by the drum rotation drive motor 236 according to the rotation chart for the rinsing process. Is done. After the intermediate dehydration step and the rinsing step are repeated a plurality of times, the process proceeds to the final rinsing step. In the final rinsing step, the water supply valve 208 is opened, and water containing a softening finish is supplied to the water tank 220.

  When the final rinsing process is completed, the drain valve 206 is opened and the rinsing liquid is discharged out of the main body 210. When the drainage is completed, a final dewatering process is performed in which the rotating drum 230 is rotated at high speed according to the rotation chart for the final dewatering process. In the final dewatering step, the rinsing liquid contained in the laundry is discharged to the inner wall surface of the water tank 220 through the small holes 235 provided in the peripheral wall of the rotating drum 230 by the centrifugal force generated by the high-speed rotation of the rotating drum 230 as in the intermediate dewatering step. Is done.

  When the final dehydration process is completed, the process proceeds to the drying process. In the drying process, the rotating drum 230 is rotated, and the heating and dehumidifying device 400 and the air blowing mechanism unit 244 are driven.

  When the Stirling engine 410 of the heating and dehumidifying device 400 is driven, heat is exchanged so that the gas is heated in the heating fins 421, and heat is exchanged so that the gas is cooled in the cooling fins 431.

  By driving the heating / dehumidifying device 400 and the air blowing mechanism 244, the gas heated by the heating fin 421 flows through the hot air path 241 as indicated by the two-dot chain line arrow in FIG. It flows into the inside of the water tank 220 through the hot air path part 247 in the water tank from 245 and blows into the rotating drum 230 (FIG. 2) disposed inside the water tank 220. The gas comes into contact with the laundry in the rotating drum 230 (FIG. 2), then flows out of the rotating drum 230 through the small hole 235, and passes through the exhaust port 246 formed in the lower part of the water tank 220. Exhaust into the humid air passage 242. The gas exhausted to the wet air passage portion 242 has high humidity due to moisture contained in the laundry in the rotating drum 230. The gas containing moisture flows as indicated by the one-dot chain line arrow in FIG. 5, returns to the cooling fin 431, is cooled by the cooling fin 431, and is dehumidified. The moisture removed from the gas is discharged from the main body 210 through the drain pipe (not shown) from below the cooling fins 431. The dehumidified gas returns to the heating fin 421 through the circulation path 243. A drying process is performed by repeating this cycle.

  As described above, the washing / drying machine 200 flows out the gas from the rotary drum 230 for storing the laundry, the hot air path portion 241 for allowing the gas to flow into the rotary drum 230, and the rotary drum 230. A hot air path section 242 for heating, a high temperature side heat exchange section 420 for heating the gas flowing through the hot air path section 241, and a low temperature side heat exchange for cooling the gas flowing through the wet air path section 242 Unit 430, and a Stirling engine 410 including a heat generating head 411 and a heat absorbing head 412. The high temperature side heat exchanging unit 420 performs heat exchange so as to heat the gas with the heat generating head 411 of the Stirling engine 410, and the low temperature side The heat exchanging unit 430 performs heat exchange so that the heat is absorbed by the heat absorbing head 412 of the Stirling engine 410.

  Conventionally, in a heat pump used in a dryer, heat is exchanged between a condensing unit that compresses a refrigerant by a compressor to change from gas to liquid and an evaporation unit that expands the refrigerant to change from liquid to gas. Yes. That is, in the heat pump, the refrigerant moves from the condensing unit through the pipe or the like to the evaporating unit, changes from liquid to gas, and moves from the evaporating unit through the pipe or the like to the condensing unit to change from gas to liquid. It is necessary to repeat changing.

  On the other hand, the Stirling engine reciprocates the displacer in the cylinder, thereby compressing the working gas such as helium in the compression space to heat the heat generating head and expand the heat generating head to cool the heat absorbing head. As described above, in the Stirling engine, the working gas remains in a gaseous state and moves only between the compression space and the expansion space. The compression space and the expansion space are disposed at both ends of one cylinder, for example. In this case, the working gas reciprocates from one end of the cylinder to the other end while maintaining the gaseous state. .

  Thus, in the Stirling engine, since it is not necessary to change the state of the refrigerant between the gas and the liquid, the responsiveness of the Stirling engine is higher than that of the heat pump. For example, the time required from the start of driving the Stirling engine until the heat generating head and the heat absorbing head reach a predetermined temperature, the evaporation unit and the condensing unit are set to a predetermined temperature after starting the heat pump. It is shorter than the time required to become.

  Therefore, by using a Stirling engine, a start-up operation for a long time is unnecessary before starting the drying operation or at the start of the drying operation, so the controllability is higher than the heat pump, and energy saving, that is, it is easy to reduce energy consumption, A dryer that facilitates energy saving is obtained. Thus, a dryer equipped with a Stirling engine can shorten the time required to start the dryer, and, like a heat pump, it is necessary to wait for the time until the refrigerant becomes a uniform gas from the mixture of gas and liquid. Therefore, once the operation is interrupted during the operation of the dryer, the time required for starting again can be shortened.

  Further, the vibration system of the heat pump used in the conventional heat dehumidifying apparatus is a complicated vibration system including rotation vibration because a compressor is used for compression and expansion of the refrigerant. On the other hand, a Stirling engine has a simple vibration system compared to a heat pump. That is, in the Stirling engine, only a linear motion of reciprocation of the displacer is performed.

  Thus, since the Stirling engine has a simple vibration system, it is easy to absorb vibration. For example, the vibration can be easily suppressed by providing a vibration absorbing member such as a spring having the co-frequency of the displacer as the natural frequency. In a Stirling engine, vibration can be easily suppressed, so that noise due to vibration is less likely to occur.

  By doing this, vibration and noise can be reduced, usability, i.e., easy to use, energy saving, i.e., energy consumption can be effectively reduced, and heat dehumidification device that facilitates energy saving. 400 can be provided.

  The heating and dehumidifying device 400 includes a circulation path part 243 for allowing gas to flow from the wet air path part 242 to the hot air path part 241, and the gas is cooled in the low temperature side heat exchange part 430 and passes through the circulation path part 243. Then, it flows into the warm air path section 241 and is heated in the high temperature side heat exchanging section 421.

  In this way, the gas that has flowed out into the wet air path section 242 is cooled in the low temperature side heat exchange section 430, flows into the hot air path section 241 through the circulation path section 243, and is heated in the high temperature side heat exchange section 421. Therefore, it can dehumidify efficiently.

  The washer / dryer 200 is disposed so as to cover the rotary drum 230 and includes a water tank 220 for containing water. The rotary drum 230 is rotatably supported in the water tank 220 and is accommodated in the rotary drum 230. The laundry to be performed can be washed in the rotating drum 230.

  By doing in this way, it can dry quickly after completion | finish of washing. Further, in the Stirling engine 400, the high temperature portion and the low temperature portion are not separately formed, for example, connected to the Stirling engine main body by piping, and a compressor, an expansion valve, a high temperature portion (condensing portion), a low temperature portion necessary for the heat pump are formed. Since there is no need for a pipe for circulating the refrigerant connecting to the (evaporating part) and the structure is simple, the pipe breaks even when the washing / drying machine 200, which is complex and easily generates large vibration during washing, vibrates. In addition, it is possible to provide a highly reliable washing / drying machine 200 that is less prone to malfunction.

  In the washing / drying machine 200, a regenerator tube 148 is provided between the heat generating head 411 and the heat absorbing head 412, and the heat generating head 411, the heat absorbing head 412 and the regenerator tube 148 are arranged coaxially. The heat absorption head 412 and the regenerator tube 148 are arranged in the circulation path.

  In this way, the circulation path can be shortened to suppress the pressure deficit, and the thermal effect of the heat generating head 411 and the heat absorbing head 412 on each other can be reduced by the air layer around the regenerator tube 148. be able to.

  In this embodiment, the heat dehumidifying apparatus is used for a washing dryer, but the heat dehumidifying apparatus of the present invention may be used for a tableware dryer, a tableware washing dryer, a dehumidifier, a bathroom dryer, or the like.

(Embodiment 1-2)
FIG. 6: is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing / drying machine is provided as Embodiment 1-2 of this invention.

  As shown in FIG. 6, the heating and dehumidifying apparatus 500 includes a Stirling engine 510, a high-temperature side heat exchange unit 520 as a first heat exchange unit, and a low-temperature side heat exchange unit 530 as a second heat exchange unit. The Stirling engine 510 includes a heat generating head 511 and a heat absorbing head 512. The configuration and operation of the Stirling engine 510 are the same as those of the Stirling engine 100 shown in FIG. The high temperature side heat exchanging unit 520 includes a heating unit 522 for heating a gas, and a heat conduction medium channel 523 through which a heat conduction medium for conducting the heat of the heat generating head 511 to the heating unit 522 flows. The low temperature side heat exchanging unit 530 includes a cooling unit 532 for cooling the gas, and a heat conduction medium channel 533 through which a heat conduction medium for conducting the heat of the cooling head 512 to the cooling unit 532 flows. For example, water is used as the heat conduction medium. The heating unit 522 and the cooling unit 532 are both plate-shaped in this embodiment, but may be in other forms. Moreover, although the heat conductive medium flow path 523 and the heat conductive medium flow path 533 are tubular in this embodiment, other forms may be used. The heating and dehumidifying device 500 includes this main body, and a warm air side path portion and a humid air side path portion shown in FIG.

  As described above, in the heating and dehumidifying apparatus 500, the high temperature side heat exchanging unit 520 has a heating unit 522 for heating the gas and a heat conduction medium for conducting the heat of the heat generating head 511 to the heating unit 522. A heat transfer medium flow path 523. The low temperature side heat exchanging unit 530 includes a cooling unit 532 for cooling the gas, and a heat conduction medium channel 533 through which a heat conduction medium for conducting the heat of the heat absorbing head 512 to the cooling unit 532 flows. .

  By doing in this way, the position and shape of the high temperature side heat exchange part 520 and the low temperature side heat exchange part 530 are matched with the shape of the warm air path part 241 (FIG. 5) and the humid air path part 242 (FIG. 5). Optimization.

  Other configurations and effects of the washer-dryer 200 of Embodiment 1-2 are the same as those of Embodiment 1-1.

(Embodiment 1-3)
FIG. 7: is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing / drying machine is provided as Embodiment 1-3 of this invention.

  As shown in FIG. 7, the heating and dehumidifying apparatus 600 includes a Stirling engine 610, a high-temperature side heat exchange unit 620 as a first heat exchange unit, and a low-temperature side heat exchange unit 630 as a second heat exchange unit. The Stirling engine 610 includes a heat generating head 611 and a heat absorbing head 612. The configuration and operation of the Stirling engine 610 are the same as those of the Stirling engine 100 shown in FIG.

  The high temperature side heat exchanging unit 620 includes heating fins 621 connected to the heat generating head 611 as fins. The heating fin 621 has a disk shape, and the central portion is directly connected to the heat generating head 611.

  The low temperature side heat exchanging unit 630 includes a cooling unit 632 for cooling the gas, and a heat conduction medium flow path 633 for circulating a heat conduction medium for conducting the heat of the cooling head 612 to the cooling unit 632. For example, water is used as the heat conduction medium. The cooling unit 632 has a plate shape in this embodiment, but may have other forms. In addition, the heat conduction medium flow path 633 is tubular in this embodiment, but may have other forms.

  The heating and dehumidifying device 600 includes this main body, and a warm air side path portion and a humid air side path portion shown in FIG.

  Thus, in the heat dehumidifying apparatus 600, the heat generating head 611 is arranged in the hot air path portion.

  By doing so, a path for transferring heat between the heat generating head 611 and the high temperature side heat exchanging part 620 becomes unnecessary, and heat is wasted in the path between the heat generating head 611 and the high temperature side heat exchanging part 620. Can be prevented from being consumed.

  In the heating and dehumidifying apparatus 600, the high temperature side heat exchanging unit 620 includes heating fins 621 arranged so as to be in contact with the heating head 611.

  By doing in this way, gas can be efficiently heat-exchanged in the heating fin 621. Moreover, the heat dehumidifying apparatus 600 can be reduced in size.

  In the heat dehumidifying apparatus 600, the low temperature side heat exchanging unit 630 includes a cooling unit 632 for cooling the gas and a heat conduction through which a heat conduction medium for conducting the heat of the heat absorbing head 612 to the cooling unit 632 flows. Medium flow path 633.

  By doing so, for example, it becomes easy to reduce the thermal effects exerted on each other by separating the heating head 611 and the heating fins 621 and the cooling unit 632 on the air path. Further, the position and shape of the cooling unit 632 such as the arrangement of the cooling unit 632 in the surplus space are optimized in accordance with the shape of the wet air passage unit 242 (FIG. 5) and the overall component arrangement of the washing / drying machine 200. It becomes easy.

  Other configurations and effects of the washer-dryer 200 of Embodiment 1-3 are the same as those of Embodiment 1-1.

(Embodiment 1-4)
FIG. 8: is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing / drying machine is provided as Embodiment 1-4 of this invention.

  As shown in FIG. 8, the heating and dehumidifying device 700 includes a Stirling engine 710, a high-temperature side heat exchange unit 720 as a first heat exchange unit, and a low-temperature side heat exchange unit 730 as a second heat exchange unit. The Stirling engine 710 includes a heat generating head 711 and a heat absorbing head 712. The configuration and operation of the Stirling engine 710 are the same as those of the Stirling engine 100 shown in FIG.

  The high temperature side heat exchanging unit 720 includes a heating unit 722 for heating a gas, and a heat conduction medium flow path 723 for flowing a heat conduction medium for conducting the heat of the heat generating head 711 to the heating unit 722. . For example, water is used as the heat conduction medium. The heating unit 722 has a plate shape in this embodiment, but may have other forms. In addition, the heat conduction medium flow path 723 is tubular in this embodiment, but may have other forms.

  The low temperature side heat exchange part 730 has the cooling fin 731 connected to the heat absorption head 712 as a fin. The cooling fin 731 has a disk shape, and the central portion is directly connected to the heat absorbing head 712.

  The heating and dehumidifying device 700 includes this main body, and a warm air side path section and a humid air side path section shown in FIG.

  As described above, the heat dehumidifying apparatus 700 is configured such that the heat absorbing head 712 is disposed in the humid air path portion.

  By doing so, a path for transferring heat between the heat absorbing head 712 and the low temperature side heat exchanging unit 730 becomes unnecessary, and heat is wasted in the path between the heat absorbing head 712 and the low temperature side heat exchanging unit 730. It is possible to prevent consumption.

  As described above, in the heating and dehumidifying apparatus 700, the low temperature side heat exchanging unit 730 includes the cooling fins 731 disposed so as to be in contact with the heat absorbing head 712.

  By doing in this way, heat can be efficiently exchanged in the cooling fins 731. Moreover, the heat dehumidifying apparatus 700 can be reduced in size.

  In the heating and dehumidifying apparatus 700, the high temperature side heat exchanging unit 720 includes a heating unit 722 for heating a gas and a heat conduction medium flow through which a heat conduction medium for conducting the heat of the heating head 711 to the heating unit 722 flows. Path 723.

  By doing so, for example, it becomes easy to reduce the thermal influence exerted on each other by separating the distance on the air path between the heating unit 722, the heat absorbing head 712, and the cooling fin 731. Further, the position and shape of the heating unit 722 such as the arrangement of the heating unit 722 in the surplus space are optimally matched to the shape of the warm air path unit 241 (FIG. 5) and the overall component arrangement of the washing / drying machine 200. It becomes easy to make.

  Other configurations and effects of the washer-dryer 200 of Embodiment 1-4 are the same as those of Embodiment 1-1.

Embodiment 1-5
FIG. 9 is a side sectional view schematically showing a side section of a washing / drying machine provided with the heating / dehumidifying device of the present invention as Embodiment 1-5 of the present invention, and FIG. 10 is a view of the washing / drying machine from the back side. FIG.

  As shown in FIGS. 9 and 10, the washing / drying machine 300 includes a main body 310, a water tank 320 attached to the inside of the main body 310, and a container for storing laundry as an object to be dried. A rotating drum 330 rotatably supported inside.

  An outer door 301 is attached to the upper surface of the main body 310. By opening the outer door 301, the laundry is put into the rotating drum 330 through the loading slot 302 (not shown) provided in the water tub 320 and the rotating drum 330 or rotated from the laundry loading port 302 provided on the upper surface of the main body 310. The laundry 330 can be taken out from the drum 330 and the laundry input port 302 can be closed by closing the outer door 301.

  The rotating drum 330 is supported inside the water tank 320 so as to rotate around a shaft portion 331 extending substantially horizontally. In this way, the drum type washing and drying machine 300 has a double structure constituted by the water tank 320 and the rotating drum 330. The shaft portion 331 is disposed on each of the left and right sides of the rotating drum 330 and includes a shaft of a drum rotation driving motor 336 for rotating the rotating drum 330. Note that the drum rotation drive motor may be provided only on one side as long as a desired driving force can be obtained.

  The inner peripheral wall surface of the water tank 320 and the outer peripheral wall surface of the rotating drum 330 form a warm air path part 341 as a first air path and a wet air path part 342 as a second air path. An intake port 345 and an exhaust port 346 are provided below the water tank 320. The intake port 345 and the exhaust port 346 may be provided in the upper part or the side part. The exhaust port 346 and the intake port 345 are connected via a circulation path part 343 as a circulation path outside the water tank 320. In the circulation path part 343, a heat dehumidifying device 400 including a blower mechanism part 344 and a Stirling engine 410 is arranged.

  Inside the main body 310 of the washing / drying machine 300, a hot air path portion 341 and a wet air path portion 342 are arranged on the side surface side of the rotary drum 330. The warm air path portion 341 and the humid air path portion 342 communicate with the inside of the water tank 320 through the intake port 345 and the exhaust port 346, respectively. The hot air path unit 341 and the wet air path unit 342 are connected to each other below the water tank 320 via the circulation path unit 343. In the circulation path part 343 extending substantially linearly, the main body of the heating and dehumidifying device 400 is arranged such that the cooling fins 431 are disposed on the wet air path part 342 side and the heating fins 421 are disposed on the hot air path part 341 side. , Provided. Below the water tank 320, a blower mechanism part 344 is disposed inside the wet air path part 342.

  When the Stirling engine 410 of the heating and dehumidifying device 400 is driven, heat is exchanged so that the gas is heated in the heating fins 421, and heat is exchanged so that the gas is cooled in the cooling fins 431.

  By driving the heating and dehumidifying device 400 and the air blowing mechanism unit 344, the gas heated by the heating fin 421 flows through the hot air path unit 341 as indicated by the two-dot chain line arrow in the drawing, and the intake port 345 The water flows into the water tank 320 and blows into the rotating drum 330 disposed inside the water tank 320. After the gas contacts the laundry in the rotating drum 330, the gas flows out of the rotating drum 330 through a small hole, passes through the exhaust port 346 formed in the lower part of the water tank 320, and the wet air path portion 342. Exhausted. The gas exhausted to the wet air passage portion 342 has high humidity due to moisture contained in the laundry in the rotating drum 330. The gas containing moisture flows as indicated by the one-dot chain line arrow in the figure, returns to the cooling fin 431, is cooled by the cooling fin 431, and is dehumidified. The moisture removed from the gas is drained from the main body 310 from below the cooling fins 431 through a drain pipe (not shown). The dehumidified gas returns to the heating fin 421 through the circulation path portion 343. A drying process is performed by repeating this cycle.

  Other configurations and effects of the washing / drying machine 300 according to Embodiment 1-5 are the same as those of the washing / drying machine 200 according to Embodiment 1-1.

(Embodiment 2-1)
Hereinafter, Embodiment 2-1 of this invention is demonstrated using FIG. 11 and FIG. FIG. 11 is a cross-sectional view illustrating a configuration of a water supply / drainage path of a drum type washing / drying machine including a heating / dehumidifying device according to Embodiment 2-1 of the present invention, and FIG. 12 is a drum type according to Embodiment 2-1 of the present invention. It is sectional drawing which shows the structure of the drying ventilation path | route of a washing dryer.

  As shown in FIG. 11, a front opening 1a for taking in and out laundry is formed on the front surface of a substantially rectangular parallelepiped main body 1, and a door 2 for opening and closing the insertion opening 1a can be rotated by a hinge mechanism. Is provided. Inside the main body 1, a bottomed cylindrical water tank 3 having an opening 3 a facing the charging port 1 a at one end is slanted so that the opening 3 a side is higher with respect to the back surface thereof, The opening 3 a of the water tank 3 and the charging port 1 a of the main body 1 are connected in a watertight manner with a packing 4. The water tank 3 is swingably arranged by being supported by a support device such as a damper (not shown).

  A rotating tub 5 for storing laundry is rotatably provided in the water tub 3. The rotating tub 5 has a bottomed cylindrical shape having an opening 5a opposite to the opening 3a at one end in the rotation axis direction, and is inclined so that the opening 5a side is higher than the bottom surface (back surface). is doing. A fluid balancer 6 is provided on the periphery of the opening of the rotary tank 5, and a plurality of holes are provided in the peripheral wall of the rotary tank 5. In a state where the door 2 is rotated and the input port 1a is opened, the laundry is put into the rotary tub 5 and the laundry is taken out from the rotary tub 5 through the input port 1a, the opening 3a, and the opening 5a. Done.

  A rotating shaft 5b is fixed to the bottom surface (rear surface) of the rotating tub 5, and is rotatably supported by the water tub 3 via a bearing 5c so that the rotating shaft is inclined. A drum pulley 5d is attached to the end of the rotating shaft 5b opposite to the side on which the rotating tub is attached.

  A stepped portion in which the top surface of the main body 1 is partially lowered is provided at the upper back of the main body 1, and a water supply port 7 for introducing water from the water supply into the main body 1 is disposed on the stepped portion. A water supply valve (not shown) is arranged on the downstream side of the water supply port 7, and the water supply valve is opened and closed in accordance with instructions from a control device (not shown) that controls the operation of each part of the washing machine. Be controlled. When the water supply valve is opened by an instruction from the control device, water from the water supply is introduced into the main body 1 from the water supply port 7. The water that has passed through the water supply port 7 is supplied into the detergent case 9 through the water supply channel 8 and mixed with the detergent, and then supplied into the water tank 3 through the water supply pipe 10.

  Further, a drain pipe 11 that constitutes a discharge path for the water supplied into the water tank 3 to the outside of the main body 1 is connected to the lower side of the rear side of the water tank 3. Foreign matter such as yarn waste is removed from the water discharged from the water tank 3 to the drain pipe 11 by the drain filter 12a disposed in the filter device 12. The filter device 12 is provided with an air trap 12b, and one end of a pressure guiding tube 13 communicating with the inside of the air trap 12b is connected. A water level sensor 14 is connected to the other end of the pressure guiding tube 13, and when it is easy to wash, the water level in the water tank 3 is detected by measuring the air pressure in the air trap 12 b with the water level sensor 14. . The water from which foreign matter has been removed by the filter device 12 flows into the drainage channel 15. A drain valve 16 is arranged on the downstream side of the drain passage 15, and the drain valve 16 is opened and closed in accordance with instructions from a control device (not shown) that controls the operation of each part of the washing machine, so that drainage from the inside of the main body 1 is performed. Be controlled. When the drain valve 16 is opened by an instruction from the control device, the water in the drain channel 15 is discharged out of the main body 1 through the drain hose 17. The drainage channel 15 and the drainage hose 17 are part of the drainage channel.

  As shown in FIG. 12, an installation base 18 is provided at the lower part of the water tank, and a motor 19 capable of controlling the rotation speed for rotating the rotary tank 5 is disposed on the installation base 18. A motor shaft 19 a is attached to the motor 19, and a motor pulley 20 is provided on the opposite side of the motor shaft 19 a to which the motor 19 is attached. The motor pulley 20 and the rotary tank pulley 5d are wound around the belt 21 so that the power of the motor pulley 20 can be transmitted to the rotary tank pulley 5d.

  A clutch mechanism 22 is inserted into the motor shaft 19a, and is configured to be able to switch between a state in which the rotational driving force of the motor shaft 19a is transmitted to a transmission mechanism portion 23 provided therebelow or a state in which it is not transmitted. Yes. The rotational driving force transmitted to the transmission mechanism unit 23 is supplied to the heat exchange unit 24 and used as power for the heat exchange unit 24. More detailed configurations and operations of the clutch mechanism 22, the transmission mechanism unit 23, and the heat exchange unit 24 will be described later.

  A ventilation path (circulation duct) 25 which is an example of a circulation duct through which air for drying the laundry put in the rotary tub 5 circulates is provided from the rear rear side to the lower part and front front of the water tank. In the ventilation path 25, a blower 26 and a heat exchange unit 24 that are airflow sources of the ventilation path 25 are arranged in the path. During the drying operation, the air in the water tank 3 is discharged to the ventilation path 25 through the exhaust port 25a. The air flowing into the ventilation path 25 is sent to the heat exchanging unit 24 by a blower 26 which is an example of a fan, cooled and dehumidified by a heat absorbing head 38a, which will be described later, and then heated by a heat generating head 38b. It is sent again to the water tank 3 from 25b. A part of the ventilation path 25 may be provided along the peripheral edge of the back surface of the water tank 3.

  Next, the structure of the clutch mechanism 22, the transmission mechanism part 23, and the heat exchange part 24 is demonstrated using FIGS. 13-15. 13 is an enlarged view of the main part of FIG. 12, FIG. 14 is an exploded perspective view of the clutch mechanism 22, and FIG. 15 is a view of FIG.

  As shown in FIG. 13, the clutch mechanism 22 includes an interlocking shaft 27, a clutch piece 28, a coil spring 29, and a solenoid 30. The interlocking shaft 27 is rotatably inserted with respect to the motor shaft 19a, and is configured such that the closer to the motor 19 has a smaller diameter and the farther has a larger diameter. As shown in FIG. 14, the small-diameter portion 27a, which is a small-diameter portion of the interlocking shaft 27, is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °. The large-diameter portion 27b, which is the large-diameter portion of the interlocking shaft 27, has a gear-like periphery, and is connected to a first interlocking gear 31 described later so that power can be transmitted. A connecting portion 19b formed integrally with the motor shaft 19a is formed adjacent to the small diameter portion 27a of the interlocking shaft 27 and closer to the motor 19 than the small diameter portion 27a of the interlocking shaft 27. As shown in FIG. 14, the connecting portion 19b is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °, and has the same shape as the small diameter portion 27a of the interlocking shaft 27. . The clutch piece 28 is made of a magnetic material. As shown in FIG. 14, the outer peripheral side is formed in a circular shape, and the inner peripheral side is formed so that a part thereof is depressed in the radial direction every 90 °. The small diameter portion 27a of the interlocking shaft 27 and the outer periphery of the connecting portion 19b are configured to fit on the inner peripheral side. A coil spring 29 is compressed and disposed between the large-diameter portion 27b of the interlocking shaft 27 and the clutch piece 28, and urges the clutch piece 28 to be engaged only with the connecting portion 19b. As shown in FIG. 13, a solenoid 30 that generates a magnetic force and generates a repulsive force on the clutch piece 28 is disposed on the outer peripheral side of the clutch piece 28. The solenoid 30 moves the clutch piece 28 against the urging force of the coil spring 29 by driving, and engages the clutch piece 28 with the connecting portion 19b and the small diameter portion 27a as shown in FIG. The urging force is adjusted so as to transmit the 19 rotational driving force to the transmission mechanism 23.

  As shown in FIG. 13, the transmission mechanism unit 23 includes a first transmission gear 31 and a second transmission gear 32. As shown in FIG. 15, the first transmission gear 31 is provided below the large-diameter portion 27 b of the interlocking shaft 27, and the outer peripheral gear and the gear of the large-diameter portion 27 b of the interlocking shaft 27 are fitted. The rotational driving force of the interlocking shaft 27 is transmitted to the second transmission gear 32 disposed below the interlocking shaft 27. As shown in FIG. 14, the second transmission gear 32 is formed so that one side in the rotation axis direction is a small-diameter portion 32a that is a small-diameter gear, and the other side is a large-diameter portion 32b that is a large-diameter gear. Yes. In the second transmission gear 32, the small diameter portion 32a is engaged with the first transmission gear 31, and the large diameter portion 32b is engaged with a shaft gear 33 described later. Communicate to The clutch mechanism 22 and the transmission mechanism unit 23 are examples of the transmission unit.

  In the present embodiment, the heat exchanging unit 24 as a heating and dehumidifying device uses a parallel type two-piston Stirling refrigerator. As shown in FIG. 13, the shaft gear 33, the crankshaft 34, the heat absorption side crank 35a, the heat generation side crank 35b, the heat absorption side piston 36a, the heat generation side piston 36b, the low temperature chamber 37a, the high temperature chamber 37b, the heat absorption head 38a, and the heat generation head 38b. And a regenerator 39. The shaft gear 33 is disposed below the large-diameter portion 32 b of the second transmission gear 32 and is engaged with the gear of the large-diameter portion 32 b of the second transmission gear 32. The shaft gear 33 is integrally attached with a crankshaft 34 that extends toward the front side of the product. The crankshaft 34 is rotatably supported at two places on the installation base 18, and a heat absorption side crank connection portion 34 a and a heat generation side crank connection portion 34 b are provided between the portions that are supported by the shaft. In FIG. 13, the heat absorption side crank connection portion 34a is bent so as to protrude upward, and the heat generation side crank connection portion 34b is bent so as to protrude toward the front side, and the shaft gear 33 is formed as shown in FIG. 1 is rotated counterclockwise (counterclockwise) as viewed from the rear, and the heat generating side crank connecting portion 34b is rotated at a phase advanced by 90 ° with respect to the heat absorbing side crank connecting portion 34a. The head 38a operates so as to cool the air in the air passage 25, and the heat generating head 38b operates to heat the air in the air passage 25.

  The heat absorption side crank connection part 34a and the heat generation side crank connection part 34b are connected to one end of the heat absorption side crank 35a and the heat generation side crank 35b. The heat absorption side crank 35a and the heat generation side crank 35b are connected to the other end of the heat absorption side piston 36a and the heat generation side piston 36b, respectively. Below the heat absorption side piston 36a and the heat generation side piston 36b, there are provided a low temperature chamber 37a and a high temperature chamber 37b in which a gas such as hydrogen or helium is sealed with the installation base 18 as an outline, respectively. The inner surface of the low greenhouse 37a and the heat generating side piston 36b and the inner surface of the high temperature chamber 37b are configured to be airtight and slidable. The tip portions protruding into the ventilation path 25 below the low greenhouse 37a and the high temperature chamber 37b function as a heat absorption head 38a that cools the air in the ventilation path 25 and a heat generation head 38b that heats the air in the ventilation path 25. The heat absorbing head 38a and the heat generating head 38b do not necessarily have to protrude into the ventilation path 25, but are preferably protruded into the ventilation path 25 in order to improve heat exchange efficiency. This cooling and heating function will be described later. Further, the low temperature chamber 37a and the high temperature chamber 37b have paths that allow the rooms to communicate with each other, and a regenerator 39 is disposed in the path. The regenerator 39 has an effect of storing heat from the high-temperature gas passing through the periphery or supplying the stored heat to the low-temperature gas. The heat absorption head 38a and the heat generation head 38b are arranged so that the arrangement directions thereof coincide with the projection axis of the rotation axis of the rotation tank 5 onto the horizontal plane, and vibration that vibrates integrally with the water tank 3 in the main body 1 during operation. The body's center of gravity is pushed down to make it easier to reduce vibration. Thereby, even when the rotating tub 5 is arranged at a high position, the laundry can be easily taken out while contributing to the noise reduction. The installation base 18 is an example of a housing.

  Next, the operation of this washing / drying machine will be described. In the washing / drying machine having the configuration, the user turns on the power, puts the laundry into the rotating tub 5 from the insertion port, and puts the detergent into the detergent case 9, and then presses a start switch on an operation panel (not shown). When the operation is started, the control unit supplies water to the water tank 3 through the water supply port 7, the water supply channel 8, the detergent case 9 and the water supply pipe 10. When the water level sensor 14 detects that the water level in the water tank 3 has reached a predetermined water level, the control unit stops water supply to the water tank 3 and drives the motor 19 to rotate the rotating tank 5 at a low speed. Perform the washing process.

  When the washing process is completed, the water in the water tank 3 is discharged out of the machine through the drainage channel 11, the filter device 12, the drainage pipe 15, the drainage valve 16 and the drainage hose 17, and then the rotating tank 5 is rotated at a high speed. To dehydrate the washing water contained in the laundry. When the dehydration process is completed, a rinsing process for rotating the rotating tank 5 at a low speed is started again after water supply to the predetermined level in the water tank 3. When the rinsing step is completed, the dewatering step is performed after the washing water in the water tank 3 is drained. After the rinsing process and the dehydrating process are repeated a plurality of times, the process proceeds to the drying process.

  Next, operation | movement of the principal part of the drying process of Embodiment 2-1 of this invention is demonstrated using FIGS. 16-19. FIG. 16 is an enlarged view of a main part in a state where the clutch mechanism 22 is switched so as to transmit the rotational driving force to the heat exchanging unit 24, and FIG. 17 is a state where the crankshaft 34 is rotated by 90 ° from the state of FIG. FIG. 18 is an enlarged view of a main part, and FIG. 19 is an enlarged view of a main part when the crankshaft 34 is rotated 180 ° from the state of FIG. 16, and FIG. 19 is a state where the crankshaft 34 is rotated 270 ° from the state of FIG. It is a principal part enlarged view.

  When the drying process is started, the blower 26 is driven to blow the air in the ventilation path 25, and the solenoid 30 is driven to engage the clutch piece 28 with the connecting portion 19b and the interlocking shaft 27. This rotational drive force can be transmitted to the interlocking shaft 27. In this state, when the motor 19 is rotated clockwise as shown in FIG. 15, the rotating tub 5 is rotated clockwise as viewed from the rear, and the interlocking shaft 27 is also rotated in the same arrow a direction. The first transmission gear 31 is rotated counterclockwise in the direction of arrow b. The rotational driving force transmitted to the first transmission gear 31 is transmitted to the second rotation gear 32 fitted to the first transmission gear 31 to rotate the second transmission gear 32 in the direction of arrow c. The second transmission gear 32 that rotates in the direction of the arrow c rotates the shaft gear 33 in the direction of the arrow d to drive the heat exchange unit 24.

  In the state of FIG. 16, while the shaft gear 33 is driven in the direction of the arrow d to reach the state of FIG. 17, the heat absorption side crank connection portion 34a and the heat generation side crank connection portion 34b are connected to the heat absorption side crank 35a and the heat generation side crank 35b. Is driven downward, and the gas in the low temperature chamber 37a and the high temperature chamber 37b is compressed by the heat absorption side piston 36a and the heat generation side piston 36b having a phase difference of 90 degrees. At this time, the compressibility of the gas in the high temperature chamber 37b is much larger than that in the low temperature chamber 37a, and the pressure and temperature of the gas in the high temperature chamber 37b increase. Therefore, the temperature of the heating head 38b increases and the high pressure in the high temperature chamber 37b increases. Then, the gas whose temperature has increased is blown into the low temperature chamber 37a through the regenerator 39. When the gas whose temperature has been increased due to the high pressure in the high temperature chamber 37b passes through the regenerator 39, the heat quantity of this gas is stored in the regenerator 39, and the cooled gas is blown into the low temperature chamber 37a. Then, the temperature of the low temperature chamber 37a is lowered.

  While the rotation of the shaft gear 33 progresses and the transition from the state of FIG. 17 to the state of FIG. 18 occurs, the heat absorption side crank connection portion 34a pushes the heat absorption side crank 35a downward. 34b drives the heat generating side crank 35b to lift upward, compresses the gas in the low temperature chamber 37a by the heat absorption side piston 36a, and expands the gas in the high temperature chamber 37b by the heat generation side piston 36b. Moves rapidly through the regenerator 39 to the high temperature chamber 37b. At this time, the gas moving to the high temperature chamber 37b is heated by the amount of heat stored in the regenerator 39, the temperature rises, and the temperature in the high temperature chamber 37b rises.

  Further, while the shaft gear 33 is rotated to shift from the state of FIG. 18 to the state of FIG. 19, the heat absorption side crank connection portion 34a and the heat generation side crank connection portion 34b are connected to the heat absorption side crank 35a (see FIG. 8). And write the lead wire) and drive the heat generating side crank 35b upward to expand the gas in the low temperature chamber 37a and the high temperature chamber 37b by the heat absorption side piston 36a and the heat generation side piston 36b. At this time, the expansion coefficient of the gas in the low temperature chamber 37a is much larger than that in the high temperature chamber 37b, and the pressure and temperature of the gas in the low temperature chamber 37a decrease, so the temperature of the heat absorbing head 38a decreases.

  Further, while the shaft gear 33 is rotated to shift from the state shown in FIG. 19 to the state shown in FIG. 16, the heat absorption side crank connection portion 34a moves upward in the direction of lifting the heat absorption side crank 35a. 34b drives the heat generating side crank 35b to push downward, expands the gas in the low temperature chamber 37a by the heat absorbing side piston 36a, and compresses the gas in the high temperature chamber 37b by the heat generating side piston 36b. Moves rapidly through the regenerator 39 to the cold chamber 37a. At this time, the amount of heat of the gas moving to the low temperature chamber 37a is stored in the regenerator 39, and the gas whose temperature has decreased is blown into the low temperature chamber 37a. As the shaft gear 33 rotates in this manner, the heat absorbing head 38a cools and the heat generating head 38b generates heat, and the temperature decreases and increases according to the rotational speed of the shaft gear 33, respectively.

  In the drying process, the air discharged from the water tank 3 into the ventilation path 25 through the exhaust port 25a is sent to the heat absorbing head 38a through the blower 26. The air sent to the heat absorbing head 38a is cooled and dehumidified by the heat absorbing head 38a, and then sent to the heat generating head 38b. The air sent to the heat generating head 38b is heated by the heat generating head 38b and blown into the water tub 3 to evaporate the moisture of the laundry in the rotating tub and advance the drying. Thereafter, the end of drying is detected by detection of a humidity sensor, a temperature sensor or the like (not shown), and the operation is terminated. A drainage hole (not shown) is provided at the bottom of the ventilation path 25 below the heat absorption head 38a. When water (drain water) is condensed on the bottom heat absorption head 38a, the ventilation path 25 and the drainage hose 17 are connected to the drainage hole from the drainage hole. Drained by a connecting drain hose.

  As described above, according to the embodiment 2-1 of the present invention, by providing the clutch mechanism 22 on the motor shaft 19a of the motor 19 that rotates the rotating tub 5, the rotational driving force of the motor 19 is applied to the heat exchange unit 24. Since it can transmit and operate the heat exchange part 24, it is not necessary to provide the electric motor which operates a reverse Stirling cycle separately, and a high energy-saving washing machine can be provided. Moreover, since the ventilation path 25 is provided in the lower part in the outer box 1, it is not necessary to provide a large space on the top surface of the outer box 1 and the upper end of the water tank 3, the height of the water tank 3 can be increased, and the laundry can be easily taken out. It can be a washing machine. Furthermore, since the center of gravity is disposed along the center line below the water tank 3, it can also act as a vibration-preventing weight and can improve the quietness. Further, since a part of the ventilation path 25 is disposed below the heat exchange unit 24 and above the drainage channel 15 or the drainage hose 17, that is, between both, drainage of drain water cooled and dehumidified by the heat exchange unit The route can be shortened and drained quickly.

(Embodiment 2-2)
Hereinafter, Embodiment 2-2 of the present invention will be described with reference to FIGS. 20 is a cross-sectional view of a drum type washer / dryer provided with the heating and dehumidifying device of the present invention according to Embodiment 2-2 of the present invention, FIG. 21 is an enlarged view of the main part of FIG. FIG. 23 is an exploded perspective view of the configuration around the motor shaft 40b. In the embodiment 2-2, the same components as those in the embodiment 2-1 are denoted by the same reference numerals and the description thereof is omitted.

  In Embodiment 2-2, a drive unit 40 and a ventilation path 41 which are examples of a motor are provided on the back surface of the water tank 3. As shown in FIG. 21, the drive unit 40 has an outer cover covered with a motor cover 40a, and a motor shaft 40b, one end of which is connected to the center of the back surface of the rotating tub 5, is freely rotatable by a bearing 40c. It is supported by. A rotor 40d is attached to the other end of the motor shaft 40b, and has an inner rotor type direct drive system configuration in which a rotational driving force is applied by a stator 40e provided on the outer periphery thereof. Yes. Further, the motor shaft 40b is provided with a connecting portion 40f in which a part of the motor shaft 40b has a large diameter. As shown in FIG. 23, the connecting portion 40f is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °.

  A ventilation path 41 is provided from the back surface of the water tank 3 to the peripheral surface. The ventilation path 41 provided on the back side is arranged so as to surround the outer periphery of the drive unit 40 in the clockwise direction from above so as to substantially follow the peripheral edge of the back surface of the water tank 3. The peripheral surface is provided so as to extend forward. As shown in FIG. 22, the ventilation path 41 is formed between an exhaust port 41a that is a communication port with the inside of the water tank 3, a casing 41b that is an outline of the ventilation path 41, a rear surface of the water tank 3, and the casing 41b. A water tank back surface path 41c, a blower 41d that is an air flow source of the air flow path 41, and a water tank peripheral surface path 41e formed between the water tank 3 peripheral surface and the casing 41b. An absorptive head 54a and a heat generating head 54b of a heat exchanging section 48, which will be described later, protrude from the aquarium back path 41c, and the air in the aquarium back path 41c is cooled and dehumidified and heated by the heat absorbing head 54a and the exothermic head 54b. To be served. Moreover, although not shown in figure, the air supply opening to the water tank 3 of the water tank peripheral surface path | route 41e is distribute | arranged so that the air which passed the ventilation path 41 may be blown in into the rotation tank 5 from the opening part 5a of the rotation tank 5. FIG. Yes. The blower 41d is an example of the fan, and the water tank back surface path 41c and the water tank peripheral surface path 41e are examples of the circulation duct.

  As shown in FIG. 21, an interlocking shaft 42 is rotatably disposed on the outer periphery of the motor shaft 40b adjacent to the connecting portion 40f. As shown in FIG. 23, the interlocking shaft 42 is configured such that a portion adjacent to the connecting portion 40f has a small diameter and a portion away from the connecting portion 40f has a large diameter. As shown in FIG. 23, the small-diameter portion 42a, which is a small-diameter portion of the interlocking shaft 42, is formed in a cross-shaped cross section so that a part protrudes in the radial direction every 90 °, and is formed in the same shape as the connecting shaft 40f. Has been. In contrast, the large-diameter portion 42b, which is the large-diameter portion of the interlocking shaft 42, is formed in a gear shape, and this gear is connected to a transmission gear 46, which will be described later, so as to transmit the rotational driving force. Yes.

  As shown in FIG. 21, a clutch piece 43 is provided on the outer periphery of the connecting shaft 40f. The clutch piece 43 is made of a magnetic material. As shown in FIG. 23, the outer peripheral side is formed in a circular shape, and the inner peripheral side is formed so as to be partially recessed in the radial direction every 90 °. The small-diameter portion 42a of the interlocking shaft 42 and the outer periphery of the connecting portion 40f are configured to fit on the inner peripheral side. A coil spring 44 is compressively disposed between the large-diameter portion 42b of the interlocking shaft 42 and the clutch piece 43, and urges the clutch piece 43 to be engaged only with the connecting portion 40f. As shown in FIG. 21, a solenoid 45 that generates a magnetic force to generate a repulsive force on the clutch piece 43 is disposed on the outer peripheral side of the clutch piece 43. The solenoid 45 moves the clutch piece 43 against the urging force of the coil spring 44 by driving, and causes the clutch piece 43 to be fitted to both the connecting portion 40f and the interlocking shaft 42 so that the rotational driving force of the motor shaft 40b is described later. The urging force is adjusted so as to be transmitted to the transmission gear 46.

  A transmission gear 46 is disposed below the large-diameter portion 42b of the interlocking shaft 42 as shown in FIG. The transmission gear 46 is connected to the gear of the large-diameter portion 42b of the interlocking shaft 42 above the transmission gear 46, and is also connected to the gear portion of the crank gear 47 provided below the transmission gear 46. The crank gear 47 is perpendicular to the surface of the small diameter gear portion 47a (the broken line portion in FIG. 23), the disk-shaped large diameter portion 47b, and the surface of the large diameter portion 47b opposite to the surface on which the gear portion 47a is provided. It is comprised from the cylindrical crankpin 47c which protrudes. A heat exchanging portion 48 is provided below the crank gear 47 as shown in FIG. The interlocking shaft 42, the clutch piece 43, the coil spring 44, the solenoid 45, the transmission gear 46, and the crank gear 47 are examples of the transmission unit.

  Here, the heat exchange part 48 is demonstrated using FIG. 24 is a cross-sectional view taken along the line CC of FIG.

  As the heat dehumidifying device, the heat exchanging unit 48 uses a V-type two-piston Stirling refrigerator in the present embodiment. As shown in FIG. 24, the outer shell is integrally formed with the motor cover 40a, the heat absorption side crank 49a, the heat generation side crank 49b, the heat absorption side cross head 50a, the heat generation side cross head 50b, the heat absorption side piston pin 51a, the heat generation. Side piston pin 51b, heat absorption side piston 52a, heat generation side piston 52b, low temperature chamber 53a, high temperature chamber 53b, heat absorption head 54a, heat generation head 54b, low temperature chamber air inlet / outlet 55a, high temperature chamber air inlet / outlet 55b, low temperature air passage 56a, high temperature air A passage 56b and a regenerator 57 are provided.

  One end of each of the heat absorption side crank 49a and the heat generation side crank 49b is rotatably connected to the crank pin 47c. On the other hand, the other ends of the heat absorption side crank 49a and the heat generation side crank 49b are rotatably connected to the heat absorption side cross head 50a and the heat generation side cross head 50b, and transmit the rotational driving force of the motor 40 transmitted from the crank pin 47c. . The heat absorption side cross head 50a and the heat generation side cross head 50b are fitted in a swingable manner with the inner peripheral surface of the cylindrical motor cover 40a, and are transmitted from the heat absorption side crank 49a and the heat generation side crank 49b. The driving force is transmitted in the axial direction of each piston pin to the heat absorption side piston pin 51a and the heat generation side piston pin 51b connected to the heat absorption side crosshead 50a and the heat generation side crosshead 50b. The heat absorption side piston pin 51a and the heat generation side piston pin 51b are arranged so that the axial directions thereof are substantially perpendicular when viewed from the back side of the water tank 3.

  Further, one end of the heat absorption side piston pin 51a and the heat generation side piston pin 51b is connected to the heat absorption side cross head 50a and the heat generation side cross head 50b, and the other end is connected to the heat absorption side piston 52a and the heat generation side piston 52b. . The heat absorption side piston 52a and the heat generation side piston 52b are slidable with the inner peripheral surface of the motor cover 40a formed in a cylindrical shape, and between the heat absorption side piston 52a and the heat generation side piston 52b and the inner peripheral surface of the motor cover 40a. These sliding surfaces are fitted so as to be hermetically sealed. A low temperature chamber 53a and a high temperature chamber 53b are provided on the side of the heat absorption side piston 52a and the heat generation side piston 52b opposite to the surface on which the heat absorption side piston pin 51a and the heat generation side piston pin 51b are attached. The tip end side is closed by the heat absorbing head 54a and the heat generating head 54b.

  The low greenhouse 53a and the high temperature chamber 53b have a low temperature room air inlet / outlet 55a and a high temperature room air inlet / outlet 55b that open toward the rear side of the main body, and the low temperature through the low temperature room air inlet / outlet 55a and the high temperature room air inlet / outlet 55b, respectively. The air passage 56a and the hot air passage 56b communicate with each other. A regenerator 57 is connected to a path between the low temperature air passage 56a and the high temperature air path 56b. The air in the low greenhouse 53a is sent to the high temperature chamber 53b through the low temperature chamber air inlet / outlet 55a, the low temperature air passage 56a, the regenerator 57, the high temperature air path 56b, and the high temperature chamber air inlet / outlet 55b by the operation of the heat absorption side piston 52a. Conversely, the air in the high temperature chamber 53b is moved to the low temperature chamber 53a through the high temperature chamber air inlet / outlet 55b, the high temperature air passage 56b, the regenerator 57, the low temperature air path 56a, and the low temperature chamber air inlet / outlet 55a by the operation of the heat generating side piston 52b. Sent. At this time, the regenerator 57 absorbs the heat of the air flowing from the high temperature air path 56b and discharges the heat to the air flowing from the low temperature air path 56a, so that the air in the low temperature chamber 53a is low and the air in the high temperature chamber 53b is Acts to maintain high temperatures.

  Next, operation | movement of the principal part of the drying process of Embodiment 2-2 of this invention is demonstrated using FIG. 22, FIG. 24-FIG. FIG. 25 is an enlarged view of a main part when the crank gear 47 is rotated 90 ° from the state of FIG. 24, and FIG. 26 is an enlarged view of a main part of the state where the crank gear 47 is rotated 180 ° from the state of FIG. FIG. 27 is an enlarged view of a main part in a state where the crank gear 47 is rotated by 270 ° from the state of FIG.

  When the drying process is started, the blower 41d is driven to blow air in the ventilation path 41, and the solenoid 45 is driven to engage the clutch piece 43 with the connecting portion 40f and the interlocking shaft 42, thereby driving the driving portion. Forty rotational driving forces can be transmitted to the interlocking shaft 42. In this state, when the drive unit 40 is rotated in the direction of the arrow e, which is clockwise as shown in FIG. 22, the rotating tub 5 is rotated clockwise around the motor shaft 40b when viewed from the rear, and interlocked. The shaft 42 is also rotated in the same arrow e direction, and the transmission gear 46 is rotated in the counterclockwise arrow f direction. The rotational driving force transmitted to the transmission gear 46 rotates the crank gear 47 fitted thereto in the direction of the arrow g to drive the heat exchanging unit 48.

  In the state of FIG. 24, while the crank gear 47 is driven in the direction of arrow g in FIG. 22 (shown in FIG. 14) and enters the state of FIG. 25, the heat absorption side crank 49a lifts the heat absorption side crosshead 50a upward. The heat generation side crank 49b drives the heat generation side crosshead 50b to push downward, expands the gas in the low temperature chamber 53a by the heat absorption side piston 52a, and expands the gas in the high temperature chamber 53b by the heat generation side piston 52b. In order to compress the gas, the gas in the high temperature chamber 52b moves rapidly through the regenerator 57 to the low temperature chamber 53a. At this time, the amount of heat of the gas moving to the low temperature chamber 52a is stored in the regenerator 57, and the gas whose temperature has decreased is blown into the low temperature chamber 52a.

  While the rotation of the crank gear 47 advances and the state of FIG. 25 shifts to the state of FIG. 26, the heat absorption side crank 49a and the heat generation side crank 49b are connected to the heat absorption side cross head 50a and the heat generation side cross head 50b. Driven upward, the gas in the low temperature chamber 53a and the high temperature chamber 53b is expanded by the heat absorption side piston 52a and the heat generation side piston 52b. At this time, the expansion coefficient of the gas in the low temperature chamber 53a is much larger than that in the high temperature chamber 53b, and the pressure and temperature of the gas in the low temperature chamber 53a decrease, so the temperature of the heat absorbing head 54a decreases.

  While the rotation of the crank gear 47 advances and the state of FIG. 26 shifts to the state of FIG. 27, the heat absorption side crank 49a pushes the heat absorption side crosshead 50a downward, and the heat generation side crosshead 49b The heat generation side crank 50b is driven upward, the gas in the low temperature chamber 53a is compressed by the heat absorption side piston 52a, and the gas in the high temperature chamber 53b is expanded by the heat generation side piston 52b, so that the gas in the low temperature chamber 53a is regenerated. It moves rapidly through the vessel 57 to the high temperature chamber 53b. At this time, the gas moving to the high temperature chamber 53b is heated by the amount of heat stored in the regenerator 57, the temperature rises, and the temperature in the high temperature chamber 53b rises.

  While the rotation of the crank gear 47 advances and the transition from the state of FIG. 27 to the state of FIG. 24 is performed, the heat absorption side crank 49a and the heat generation side crank 49b move the heat absorption side cross head 50a and the heat generation side cross head 50b. The gas is driven in a downward direction and compressed in the low temperature chamber 53a and the high temperature chamber 53b by the heat absorption side piston 52a and the heat generation side piston 52b. At this time, the compressibility of the gas in the high temperature chamber 53b is much larger than that in the low temperature chamber 53a, and the pressure and temperature of the gas in the high temperature chamber 53b increase. Therefore, the temperature of the heat generating head 54b increases and the high pressure in the high temperature chamber 53b increases. Then, the gas whose temperature has increased is blown into the low temperature chamber 53a through the regenerator 57. When the gas whose temperature has been increased due to the high pressure in the high temperature chamber 53b passes through the regenerator 57, the heat quantity of this gas is stored in the regenerator 57, and the cooled gas is blown into the low temperature chamber 53a by depriving the heat quantity. Then, the temperature of the low temperature chamber 53a is lowered. As the crank gear 47 rotates in this manner, the heat absorbing head 54a cools and the heat generating head 54b generates heat, and the temperature decreases and rises according to the rotational speed of the crank gear 47, respectively.

  In the drying process, the air discharged from the water tank 3 into the ventilation path 41 through the exhaust port 41a is sent to the heat absorbing head 54a through the blower 41c. The air sent to the heat absorbing head 54a is cooled and dehumidified by the heat absorbing head 54a, and then sent to the heat generating head 54b. The air sent to the heat generating head 54b is heated by the heat generating head 54b and blown into the water tub 3 through the air supply port described above to evaporate the moisture of the laundry in the rotating tub and proceed with drying. Let Thereafter, the end of drying is detected by detection of a humidity sensor, a temperature sensor or the like (not shown), and the operation is terminated. A drain hole (not shown) is provided at the bottom of the water tank back path 41C below the heat absorbing head 54a. When water (drain water) condensed on the heat absorbing head 54a is dropped, the water tank back path 41C and the drain hose 17 are discharged from the water drain hole. It is drained by a drain hose that connects the two.

  As mentioned above, according to Embodiment 2-2 of this invention, in addition to the effect by Embodiment 2-2 mentioned above, the empty space below the direct drive type drive part 40 provided in the water tank 3 back surface In addition, since the heat exchanging portion 48 can be arranged through the clutch mechanism so that the reverse Stirling cycle has a substantially inverted V shape or C shape, a space-saving washing machine can be provided.

  In addition, in order to facilitate the removal of the laundry, when applied to the construction of a drum-type washing machine in which the openings of the water tub 3 and the rotating tub 5 are arranged obliquely upward, the water tank 3 and the lower part of the main body 1 The space can be used effectively, and the center of gravity is lowered because the heat exchanging unit 40 is disposed below the driving unit 40. In addition, the heat absorption head 54a side and the heat generation head 54b side of the heat exchange unit 48 are arranged in a substantially reverse V-order shape across a vertical center line passing through the motor shaft 58b of the drive unit 40 which is a heavy object, so that vibrations It can also act as a weight for prevention, and can improve the quietness.

(Embodiment 2-3)
Embodiment 2-3 of the present invention will be described below with reference to FIGS. 28 is a cross-sectional view of a drum type washer / dryer provided with the heating and dehumidifying device of the present invention according to Embodiment 2-3 of the present invention, FIG. 29 is an enlarged view of the main part of FIG. 28, and FIG. FIG. 31 is an exploded perspective view of the configuration around the motor shaft 58b. In addition, in this Embodiment 2-3, the same code | symbol is attached | subjected about the same structure as 1st, Embodiment 2-2, and description is abbreviate | omitted.

  In Embodiment 2-3, the drive part 58 which is an example of a motor is provided in the back surface of the water tank 3. FIG. As shown in FIG. 29, the drive unit 58 is covered with a motor cover 58a, and a motor shaft 58b, one end of which is connected to the center of the back surface of the rotary tub 5, is freely rotatable by a bearing 58c. It is supported by. A rotor 58e is attached to the other end of the motor shaft 58b, and has a configuration of an outer rotor type direct drive system in which a rotational driving force is applied by a stator 58d provided on the outer peripheral side thereof. Yes. Further, the motor shaft 58b is provided with a connecting portion 58f in which a part of the motor shaft 58b has a large diameter. As shown in FIG. 31, the connecting portion 58f is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °.

  On the outer periphery of the motor shaft 58b, as shown in FIG. 29, an interlocking shaft 59 is rotatably disposed adjacent to the connecting portion 58f. The interlocking shaft 59 is configured such that a portion adjacent to the connecting portion 58f has a small diameter, and a separated portion has a large diameter. As shown in FIG. 31, the small-diameter portion 59a, which is a small-diameter portion of the interlocking shaft 59, is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °, and has the same shape as the connecting shaft 58f. Has been. On the other hand, the large-diameter portion 59b, which is the large-diameter portion of the interlocking shaft 59, is formed in a gear shape, and this gear is connected to a connecting gear 63, which will be described later, so as to transmit a rotational driving force. Yes.

  As shown in FIG. 29, a clutch piece 60 is provided on the outer periphery of the connecting shaft 58f. The clutch piece 60 is made of a magnetic material. As shown in FIG. 31, the outer peripheral side is formed in a circular shape, and the inner peripheral side is formed so that a part thereof is depressed in the radial direction every 90 °. The small diameter portion 59a of the interlocking shaft 59 and the outer periphery of the connecting portion 58f are configured to fit on the inner peripheral side. A coil spring 61 is compressed between the large-diameter portion 59b of the interlocking shaft 59 and the clutch piece 60, and urges the clutch piece 60 to be engaged only with the connecting portion 58f. On the outer peripheral side of the clutch piece 60, as shown in FIG. 29, a solenoid 62 that generates a magnetic force to generate a repulsive force on the clutch piece 60 is disposed. The solenoid 62 moves the clutch piece 60 against the urging force of the coil spring 61 by the drive, and engages the clutch piece 60 with both the connecting portion 58f and the interlocking shaft 59, so that the rotational driving force of the motor shaft 58b is described later. To the connecting gear 63 to be transmitted.

  A connecting gear 63 is disposed below the large-diameter portion 59b of the interlocking shaft 59 as shown in FIG. The connecting gear 63 is connected to the gear of the large-diameter portion 59b of the interlocking shaft 59 above the connecting gear 63, and is also connected to the slide gear 64 arranged in the gear shaft direction. The slide gear 64 is coupled to the first small transmission gear 65 or the transmission gear 67 below the slide gear 64, and the first small transmission gear 65 is coupled to the second small transmission gear 66 below the slide gear 64. Further, the second small transmission gear 66 and the transmission gear 67 are connected to the crank gear 68 below the second small transmission gear 66 and the transmission gear 67. The crank gear 68 projects vertically from a surface opposite to the surface on which the small-diameter gear portion 68a (the broken line portion in FIG. 31), the disk-shaped large-diameter portion 68b, and the large-diameter gear portion are provided. It is comprised from the cylindrical crankpin 68c which carries out. A heat exchanging section 48 is provided below the crank gear 68, as shown in FIG. In the present embodiment, the heat exchanging section 48 uses a V-type two-piston Stirling refrigerator as in the second embodiment. The interlocking shaft 59, the clutch piece 60, the coil spring 61, the solenoid 62, the coupling gear 63, the slide gear 64, the first small transmission gear 65, the second small transmission gear 66, the transmission gear 67, and the crank gear 68 are transmitted. It is an example of a part.

  Here, the connection gear 63 and the slide gear 64 will be described with reference to FIG. 32A is a top view of the slide gear 64, FIG. 32B is a view as viewed from the arrow F in FIG. 32A, FIG. 32C is a view as viewed from the arrow G in FIG. , (E) is a view taken in the direction of arrow H in (d), (f) is a sectional view taken along the line II in (e), (g) is a sectional view taken along the line JJ in (e), and (h) is a sectional view in (e). KK sectional drawing, (i) is LL sectional drawing of (e).

  As shown in FIGS. 32A to 32C, the slide gear 64 includes a gear portion 64b, a cylindrical portion 64a extending in the gear shaft direction from one side surface of the gear portion 64b, and a tip of the cylindrical portion 64a. A cylindrical pin portion 64c extending in a direction perpendicular to the cylinder axis and a cylindrical pin portion 64d extending in a direction opposite to the pin portion 64c are configured. As shown in FIGS. 32D to 32I, the connecting gear 63 includes a gear portion 63b, a cylindrical portion 63a extending in the gear axis direction from one side surface of the gear portion 63b, and a cylindrical axis direction of the cylindrical portion 63a. And a hole 63c into which the cylindrical part 64a is inserted, and a pin part 64d of the slide gear 64 is inserted in a spiral shape perpendicularly to the peripheral surface of the hole 63c and the pin part 64d is cylindrical. A slide hole 63d formed so as to be slidable approximately 180 degrees around the cylindrical axis of the portion 64a, and a pin portion 64c of the slide gear 64 inserted into the spiral shape perpendicularly to the peripheral surface of the hole 63c and the pin The portion 64c includes a slide hole 63e formed so as to be slidable approximately 180 degrees around the cylinder axis of the cylinder portion 64a.

  Next, the operation when the connecting gear 63 is given a rotational driving force from the interlocking shaft 59 will be described. First, when the connecting gear 63 is connected to the first small transmission gear 65, the connecting gear 63 receives a rotational driving force from the interlocking shaft 59, and the clockwise (clockwise) direction in FIG. , The pin portion 64c slides the slide hole 63e, the pin portion 64d slides the slide hole 63d about 180 degrees around the column axis of the column portion 64a, and the column portion 64a slides in a direction to come out of the hole portion 63c. . That is, the gear portion 64 b slides toward the front side in FIG. 31 to release the connection with the first small transmission gear 65 and to connect with the transmission gear 67. On the contrary, when the connecting gear 63 is connected to the transmission gear 67, the connecting gear 63 receives a rotational driving force from the interlocking shaft 59, and rotates in the counterclockwise (counterclockwise) direction in FIG. When moved, the pin portion 64c slides the slide hole 63e, the pin portion 64d slides the slide hole 63d approximately 180 degrees around the cylinder axis of the cylinder portion 64a, and the cylinder portion 64a slides in a direction to enter the hole portion 63c. That is, the gear portion 64b slides to the back side in FIG. 31 to release the connection with the transmission gear 67 and to connect with the first small transmission gear 65. In this way, regardless of whether the rotation direction of the drive unit 58 is forward or reverse, the connection with the slide gear 64 is switched to the first small transmission gear 65 or the transmission gear 67 to thereby change the crank gear 68. The rotation direction can be a constant direction.

  Next, operation | movement of the principal part of the drying process of Embodiment 2-3 of this invention is demonstrated using FIGS. 33-36. 33 is a cross-sectional view taken along the line E-E in FIG. 29, FIG. 34 is an enlarged view of a main part of the state where the crank gear 68 is rotated by 90 ° from the state of FIG. 33, and FIG. 36 is an enlarged view of a main part in a state in which the crank gear 68 is rotated by 270 ° from the state of FIG. 33. FIG.

  When the drying process is started, the blower 41d is driven to blow air in the ventilation path 41, and the solenoid 62 is driven to engage the clutch piece 60 with the connecting portion 58f and the interlocking shaft 59, thereby driving the driving portion. The rotational driving force 58 can be transmitted to the interlocking shaft 59. In this state, the rotational driving force of the drive unit 58 is changed from the interlocking shaft 59 to the coupling gear 63 to the slide gear 64 to the transmission gear 67 (or the first small transmission gear 65 to the second small transmission gear 66) to the crank gear 68. Communicated. Thereby, the crank gear 68 rotates in the counterclockwise (counterclockwise) direction in FIG. 33 and the heat exchanging unit 48 is driven.

  In the state shown in FIG. 33, while the crank gear 68 is driven in the counterclockwise (counterclockwise) direction to reach the state shown in FIG. 34, the heat absorption side crank 49a generates heat in the direction of lifting the heat absorption side crosshead 50a upward. The side crank 49b is driven to push the heat generating side crosshead 50b downward, expands the gas in the low temperature chamber 53a by the heat absorption side piston 52a, and compresses the gas in the high temperature chamber 53b by the heat generation side piston 52b. The gas in the high greenhouse 52b passes through the regenerator 57 and rapidly moves to the low temperature chamber 53a. At this time, the amount of heat of the gas moving to the low temperature chamber 52a is stored in the regenerator 57, and the gas whose temperature has decreased is blown into the low temperature chamber 52a.

  While the rotation of the crank gear 68 advances and the state shown in FIG. 34 shifts to the state shown in FIG. 35, the heat absorption side crank 49a and the heat generation side crank 49b move the heat absorption side cross head 50a and the heat generation side cross head 50b. Driven upward, the gas in the low temperature chamber 53a and the high temperature chamber 53b is expanded by the heat absorption side piston 52a and the heat generation side piston 52b. At this time, the expansion coefficient of the gas in the low temperature chamber 53a is much larger than that in the high temperature chamber 53b, and the pressure and temperature of the gas in the low temperature chamber 53a decrease, so the temperature of the heat absorbing head 54a decreases.

  While the rotation of the crank gear 68 advances and the state of FIG. 35 shifts to the state of FIG. 36, the heat absorption side crank 49a pushes the heat absorption side crosshead 50a downward, and the heat generation side crosshead 49b The heat generation side crank 50b is driven upward, the gas in the low temperature chamber 53a is compressed by the heat absorption side piston 52a, and the gas in the high temperature chamber 53b is expanded by the heat generation side piston 52b, so that the gas in the low temperature chamber 53a is regenerated. It moves rapidly through the vessel 57 to the high temperature chamber 53b. At this time, the gas moving to the high temperature chamber 53b is heated by the amount of heat stored in the regenerator 57, the temperature rises, and the temperature in the high temperature chamber 53b rises.

  While the rotation of the crank gear 68 advances and the state of FIG. 36 shifts to the state of FIG. 33, the heat absorption side crank 49a and the heat generation side crank 49b move the heat absorption side cross head 50a and the heat generation side cross head 50b. The gas is driven in a downward direction and compressed in the low temperature chamber 53a and the high temperature chamber 53b by the heat absorption side piston 52a and the heat generation side piston 52b. At this time, the compressibility of the gas in the high temperature chamber 53b is much larger than that in the low temperature chamber 53a, and the pressure and temperature of the gas in the high temperature chamber 53b increase. Therefore, the temperature of the heat generating head 54b increases and the high pressure in the high temperature chamber 53b increases. Then, the gas whose temperature has increased is blown into the low temperature chamber 53a through the regenerator 57. When the gas whose temperature has been increased due to the high pressure in the high temperature chamber 53b passes through the regenerator 57, the heat quantity of this gas is stored in the regenerator 57, and the cooled gas is blown into the low temperature chamber 53a by depriving the heat quantity. Then, the temperature of the low temperature chamber 53a is lowered. As the crank gear 68 rotates in this manner, the heat absorbing head 54a cools and the heat generating head 54b generates heat, and the temperature decreases and rises according to the rotational speed of the crank gear 68, respectively.

  In the drying process, the air discharged from the water tank 3 into the ventilation path 41 through the exhaust port 41a is sent to the heat absorbing head 54a through the blower 41c. The air sent to the heat absorbing head 54a is cooled and dehumidified by the heat absorbing head 54a, and then sent to the heat generating head 54b. The air sent to the heat generating head 54b is heated by the heat generating head 54b and blown into the water tub 3 to evaporate the moisture of the laundry in the rotating tub and advance the drying. Thereafter, the end of drying is detected by detection of a humidity sensor, a temperature sensor or the like (not shown), and the operation is terminated. A drain hole (not shown) is provided at the bottom of the water tank back path 41C below the heat absorbing head 54a. When water (drain water) condensed on the heat absorbing head 54a is dropped, the water tank back path 41C and the drain hose 17 are discharged from the water drain hole. It is drained by a drain hose that connects the two.

  As mentioned above, according to Embodiment 2-3 of this invention, in addition to the effect by Embodiment 2-1 and 2-2 mentioned above, even if the drive part 58 is rotated forward / reversely, the heat exchange part 48 is carried out. The rotation direction of the crank gear 68 for driving the motor can be set to a constant direction. Thereby, for example, in the drying process, even if the rotating tub 5 is rotated forward and backward in order to release the entanglement of clothes, the heat exchange unit 48 can continue the reverse Stirling cycle, so that uneven drying of clothes, etc. is reduced, Drying time can be shortened.

  In addition, according to Embodiments 2-1 to 2-3 of the present invention, for example, the conventional technique uses an electric heater for heating the circulating air to dry the laundry and uses tap water for cooling and dehumidifying the circulating air. In comparison, the electric power used is only the driving electric power of the motor, and the power consumption can be further reduced. In addition, the amount of tap water used can be reduced.

  In addition, according to Embodiments 2-1 to 2-3 of the present invention, for example, compared with the conventional technique using a heat pump for drying and cooling of the circulating air for drying the laundry, it is used. The power to be used is only the driving power of the motor, and the power consumption can be further reduced.

  According to Embodiments 2-1 to 2-3 of the present invention, the laundry can be dried or the laundry can be washed, dehydrated, and dried with the driving power of the motor that rotates the rotating tub. Compared to a washing and drying machine, it is possible to achieve further reduction in water saving and power consumption.

  In particular, when a Stirling refrigerator is used as the heat exchanger, a reverse Stirling cycle is performed by an interlocking means that transmits the rotational force of the motor to the Stirling refrigerator, and the low temperature chamber and the high temperature chamber of the Stirling refrigerator are used. The drying of the laundry can be realized by heating the circulating air to dry the laundry and cooling and dehumidifying the hot and humid circulating air containing moisture evaporated from the laundry.

  Therefore, it is possible to provide a dryer or a washing dryer that can further reduce power consumption without using water.

  In addition, the structure and control mentioned above may be applied not only to a washing and drying machine but also to a drying machine, and the rotary tank is not limited to a horizontal installation type, may be a vertical installation type, and is not limited to a drum type. .

  In addition, it is as follows when the technical idea of the dryer based on Embodiment 2-1 to 2-3 of this invention is summarized.

  (1) A dryer according to the present invention provides a water tank, a rotary tank rotatably provided in the water tank, a motor for rotating the rotary tank, a circulation duct communicating with the inside of the water tank, and a gas in the water tank. A fan that circulates through the circulation duct, a heat exchange part that performs heat exchange so that the air in the circulation duct is cooled by the heat absorption head and is heated by the heat generation head, and the rotational force of the motor is used to operate the heat exchange part. And a transmission unit that transmits the power for power.

  (2) The dryer according to the present invention is characterized in that the heat exchange section is provided in a water tank.

  (3) In the dryer according to the present invention, the heat exchange part is provided below the water tank.

  (4) In the dryer according to the present invention, the heat exchange part is provided on the back surface of the water tank.

  (5) The dryer according to the present invention is characterized in that the heat exchange section is provided below the motor.

  (6) The dryer according to the present invention is characterized in that at least a part of the circulation duct is disposed below the water tank.

  (7) The dryer according to the present invention is characterized in that at least a part of the circulation duct is disposed on the back surface of the water tank.

  (8) In the dryer according to the present invention, at least a part of the circulation duct is arranged along the peripheral edge of the back surface of the water tank.

  (9) The dryer according to the present invention is characterized in that a part of the circulation duct is arranged between the heat exchange part and a part of the drainage path for draining the liquid in the water tank.

  (10) The dryer according to the present invention is characterized in that the heat absorbing head and the heat generating head protrude into the circulation duct.

  (11) In the dryer according to the present invention, the heat exchange unit is a Stirling refrigerator.

  (12) In the dryer according to the present invention, the Stirling refrigerator includes a semi-hermetic housing, a crankshaft disposed in the housing, a heat absorption side crank and a heat generation side crank connected to the crankshaft, A heat absorption side piston and a heat generation side piston connected to each crank, a working gas is sealed inside, and a low temperature chamber and a high temperature chamber in which each piston reciprocates in conjunction with rotation of the crankshaft. It rotates by a part, It is characterized by the above-mentioned.

  (13) The dryer according to the present invention is characterized in that the heat absorbing head and the heat generating head are part of a low temperature chamber and a high temperature chamber that appear and disappear in the circulation duct.

  (14) In the dryer according to the present invention, the transmission unit includes an interlocking shaft that is engaged with the rotating shaft of the motor via a clutch, and a gear that is connected to the interlocking shaft and rotates the crankshaft. Features.

  (15) In the dryer according to the present invention, the transmission unit rotates the crankshaft in one direction even when the motor rotates forward or backward.

  (16) In the dryer according to the present invention, the transmission unit transmits the rotational force of the motor to the crankshaft, and operates the Stirling refrigerator in a reverse Stirling cycle.

  (17) In the dryer according to the present invention, each piston reciprocates with a phase difference of 90 degrees.

  (18) In the dryer according to the present invention, the clutch is arranged between the first fitting portion provided on the rotating shaft of the motor and the second fitting portion provided on the interlocking shaft. The urging means for urging the clutch toward the first fitting portion is disposed between the clutch and the interlocking shaft.

  (19) The dryer according to the present invention is provided with an electromagnetic coil that generates a magnetic field around the clutch, and energizes the electromagnetic coil so that the clutch is both in the first fitting portion and the second fitting portion. It moves to the position fitted in.

  (20) In the dryer according to the present invention, the gear meshes with the first transmission gear meshed with the interlocking shaft, the first transmission gear and the crank gear provided on the crankshaft, and the rotation shaft of the motor And a second transmission gear that rotates in the opposite direction.

  (21) In the dryer according to the present invention, the crankshaft includes a crankshaft in which connecting portions connected to each crank are provided with a phase difference of 90 degrees, and a crank gear provided on one of the crankshafts The second transmission gear is configured by overlapping a small-diameter gear and a large-diameter gear, and is arranged so that the first transmission gear and the small-diameter gear mesh with each other, and the crank gear and the large-diameter gear mesh with each other. It is characterized by.

  (22) In the dryer according to the present invention, the crankshaft is characterized in that a pin connected to each crank is provided on one side and a crank gear engaged with the gear is provided on the other side.

  (23) In the dryer according to the present invention, the first transmission gear is composed of an interlocking gear that is always connected to the interlocking shaft, and a slide gear that is provided with the same rotational center and position of the interlocking gear, The slide gear is provided so that the distance from the interlocking gear can be changed according to the rotation direction of the interlocking gear, the second transmission gear is always meshed with the crank gear, and the odd-numbered transmission gears having different rotational positions, When the interlocking gear rotates in one direction, the slide gear is connected to the transmission gear, and when the interlocking gear rotates in the other direction, the slide gear is small. It is connected to a transmission gear.

  (24) The dryer according to the present invention is characterized in that the low temperature chamber and the high temperature chamber are arranged in a C shape or an inverted V shape when viewed from the center of the rotating shaft of the motor.

  (25) A laundry dryer according to the present invention is any one of the above-described dryers, wherein the laundry is stored in a rotating tub, and any one of washing, dehydration, and drying is performed. .

  (26) In the washing / drying machine according to the present invention, the rotation axis of the rotating tub is substantially perpendicular to the installation surface.

  (27) In the washing / drying machine according to the present invention, the rotating shaft of the rotating tub is substantially horizontal or oblique with respect to the installation surface.

  The high controllability obtained by using an example of a Stirling engine used in the heating and dehumidifying apparatus as one embodiment of the present invention will be described.

  The characteristics of the Stirling engine and heat pump were confirmed by driving the Stirling engine and heat pump under atmospheric pressure and opening the high temperature side and low temperature side to the atmosphere. The temperature on the high temperature side of the Stirling engine was measured on the heat generating head, and the temperature on the low temperature side was measured on the heat absorbing head. The temperature on the high temperature side of the heat pump was measured in a condenser, and the temperature on the low temperature side was measured in an evaporator. The measured temperature was recorded every 10 seconds. The room temperature was about 27 ° C. The specification of the Stirling engine used as an example is an output of about 250 W, and the refrigerant is helium. Further, the specification of the heat pump used as an example is an output of about 370 W, and the refrigerant is HCF · R134a.

  FIG. 37 is a diagram showing a temporal change in temperature on the high temperature side measured immediately after the start of driving of the Stirling engine and the heat pump.

  As shown in FIG. 37, in the high temperature part of the Stirling engine, the temperature has risen immediately after the start of driving of the Stirling engine. On the other hand, the temperature of the high temperature portion of the heat pump hardly changes immediately after the start of driving of the heat pump, and starts to rise gradually after about 10 seconds.

  FIG. 38 is a diagram illustrating a temporal change in temperature on the high temperature side from the start of driving of the Stirling engine and the heat pump until reaching a predetermined temperature. The predetermined temperature was 60 ° C.

  As shown in FIG. 38, the high temperature side of the Stirling engine reached 60 ° C. in 50 seconds from the start of driving. On the other hand, the high temperature side of the heat pump reached 60 ° C. in 230 seconds from the start of driving. Thus, since the high temperature side of the Stirling engine reaches a predetermined temperature faster than the high temperature side of the heat pump, the high temperature gas is brought into contact with the laundry in the initial stage of the drying process by using the Stirling engine in the dryer. The drying time can be shortened.

  FIG. 39 is a diagram illustrating a temporal change in temperature that changes in 10 seconds with respect to the temperature on the high temperature side measured immediately after the start of driving of the Stirling engine and the heat pump.

  As shown in FIG. 39, it was found that the Stirling engine has a large temperature change amount immediately after the start of driving and has a good responsiveness. On the other hand, the temperature change of the heat pump was hardly measured immediately after the start of driving. This is because it takes a certain amount of time for the refrigerant of the heat pump to change state between the gas and liquid phases, whereas the Stirling engine does not need to change the state of the working gas, so such high responsiveness was obtained. Conceivable.

  FIG. 40 is a diagram showing temporal changes in temperature of the high temperature side and low temperature side of the Stirling engine and the high temperature side and low temperature side of the heat pump measured at intervals of 10 seconds from the start of driving of the Stirling engine and the heat pump until 2 minutes have passed. It is.

  As shown in FIG. 40, immediately after the start of driving of the Stirling engine, the temperature on the high temperature side of the Stirling engine rises quickly, the temperature on the low temperature side of the Stirling engine falls quickly, and after 50 seconds from the start of driving, The high temperature side reached 60 ° C and the low temperature side reached -20 ° C. After that, the speed of temperature change hardly decreased, and after 2 minutes from the start of driving, the high temperature side reached 80 ° C. and the low temperature side reached −60 ° C. On the other hand, the heat pump has almost no temperature change on the high temperature side and the low temperature side immediately after the start of driving, and reaches about 35 ° C. on the high temperature side and about 10 ° C. on the low temperature side from about 10 seconds to 30 seconds after the start of driving. After that, however, the amount of temperature change decreased and showed a moderate temperature change. The temperature on the high temperature side gradually increased until reaching about 48 ° C. from the start of driving for 2 minutes, but reached about 48 ° C., but the temperature on the low temperature side hardly decreased from about 8 ° C.

  Thus, the responsiveness of the Stirling engine is higher than that of the heat pump. Further, the Stirling engine has a wider controllable temperature range than the heat pump. For example, the time required from the start of driving the Stirling engine to 60 ° C on the high temperature side is less than a quarter of the time required from the start of driving the heat pump to 60 ° C on the high temperature side. there were. Therefore, by using a Stirling engine, a dryer having higher controllability than a heat pump can be obtained. As described above, the heating and dehumidifying device including the Stirling engine can shorten the time required to start the heating and dehumidifying device, and is required when the operation is once interrupted and then restarted during the operation of the heating and dehumidifying device. Time can be shortened.

  It should be considered that the embodiments and examples disclosed above are illustrative and non-restrictive in every respect. The scope of the present invention is shown not by the above embodiments and examples but by the scope of claims, and includes all modifications and variations within the meaning and scope equivalent to the scope of claims.

BRIEF DESCRIPTION OF THE DRAWINGS As Embodiment 1-1 of this invention, it is a perspective view which shows roughly the external appearance of the whole washing-drying machine provided with the heating dehumidification apparatus of this invention. It is a sectional side view which shows roughly the cross section which looked at the washing-drying machine of FIG. 1 from the direction of the II-II line. It is sectional drawing which shows the cross section of the whole Stirling engine. It is a perspective view which shows the whole main body of a heating dehumidification apparatus. It is sectional drawing which shows the outline when a washing-drying machine is seen from the direction of the VV line of FIG. As Embodiment 1-2 of this invention, it is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing-drying machine is provided. As Embodiment 1-3 of this invention, it is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing-drying machine is provided. As Embodiment 1-4 of this invention, it is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing-drying machine is provided. As Embodiment 1-5 of this invention, it is a sectional side view which shows roughly the side cross section of a washing-drying machine provided with the heating dehumidification apparatus of this invention. It is sectional drawing which shows roughly the cross section which looked at the washing-drying machine from the back surface. It is sectional drawing which shows the structure of the water supply / drainage system of the drum type washing-drying machine provided with the heating dehumidification apparatus of this invention which concerns on Embodiment 2-1 of this invention. It is sectional drawing which shows the structure of the drying processing system of the drum type washing-drying machine provided with the heating dehumidification apparatus of this invention concerning Embodiment 2-1 of this invention. It is a principal part enlarged view of FIG. It is a schematic diagram of the connection release state of a clutch mechanism. It is a schematic diagram of the connection state of the clutch mechanism and power transmission mechanism seen from A of FIG. It is a principal part enlarged view which shows the 0 degree rotation state of a crankshaft. It is a principal part enlarged view which shows the 90 degree rotation state of a crankshaft. It is a principal part enlarged view which shows the 180 degree rotation state of a crankshaft. It is a principal part enlarged view which shows the 270 degree rotation state of a crankshaft. It is a longitudinal cross-sectional view of the washing-drying machine provided with the heating dehumidification apparatus of this invention which concerns on Embodiment 2-2 of this invention. It is a principal part enlarged view of FIG. It is BB sectional drawing of FIG. It is a schematic diagram of the connection release state of a clutch mechanism. It is CC sectional drawing of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 90 degrees from the state of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 180 degrees from the state of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 270 degrees from the state of FIG. It is a longitudinal cross-sectional view of the washing-drying machine provided with the heating dehumidification apparatus of this invention which concerns on Embodiment 2-3 of this invention. It is a principal part enlarged view of FIG. It is DD sectional drawing of FIG. It is a schematic diagram of the connection release state of a clutch mechanism. It is principal part sectional drawing of a connection gearwheel and a slide gear, (a) is a top view of a slide gear, (b) is F arrow figure of (a), (c) is G arrow figure of (a), ( d) is a top view of the transmission gear, (e) is a view taken in the direction of arrow H in (d), (f) is a sectional view taken along line II in (e), (g) is a sectional view taken along line JJ in (e), (H) is KK sectional drawing of (e), (i) is LL sectional drawing of (e). It is EE sectional drawing of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 90 degrees from the state of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 180 degrees from the state of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 270 degrees from the state of FIG. It is a figure which shows the time change of the temperature of the high temperature side measured immediately after the start of a drive of a Stirling engine and a heat pump. It is a figure which shows the time change of the temperature of a high temperature side from the start of a drive of a Stirling engine and a heat pump until it reaches predetermined temperature. It is a figure which shows the time change of the temperature which changes for 10 second about the temperature of the high temperature side measured immediately after the start of a drive of a Stirling engine and a heat pump. It is a figure which shows the time change of the temperature of the high temperature side and low temperature side of a Stirling engine, and the temperature of the high temperature side and low temperature side of a heat pump which were measured at intervals of 10 seconds from the start of driving of the Stirling engine and heat pump.

Explanation of symbols

  24, 48: Heat exchange section, 25, 41: Ventilation path, 38a, 54a: Heat absorption head, 38b, 54b: Heat generation head, 100: Stirling engine, 148: Regenerator tube, 241: Hot air path section, 242: Wet Wind path section, 243: Circulation path section, 247: Warm air path section in water tank, 248: Humid air path section in water tank, 400, 500, 600, 700: Heating dehumidifier, 410, 510, 610, 710: Stirling engine 411, 511, 611, 711: heating head, 412, 512, 612, 712: heat absorption head, 420, 520, 620, 720: high temperature side heat exchange section, 421, 621: heating fin, 522, 722: heating section 430, 530, 630, 730: low temperature side heat exchange section, 532, 632: cooling section, 431, 731: cooling fins, 523, 53 , 633,723: the heat transfer medium flow path.

  The present invention relates to a heat dehumidifier.

  In recent years, there has been an increasing demand for washing and drying machines for washing clothes and the like from washing to drying. In particular, if you want to dry a small amount of laundry immediately, reduce the time to dry outdoors or indoors, or if you cannot wash during the day, you can wash your clothes at night and dry it after dehydration. Therefore, convenience according to the lifestyle of the user is evaluated.

  In such a heating and dehumidifying apparatus such as a laundry dryer, a conventionally used drying method of laundry is generally heating an electric heater or gas while rotating a rotating tub containing a laundry containing moisture. Drying is performed by supplying warm air heated by means. For example, in the water-cooled dehumidifying drier described in JP-A-63-122500 (Patent Document 1), hot and humid air during and / or after drying is directly discharged outside the apparatus, Alternatively, reflux circulation is performed in which air is cooled by a cooling and dehumidifying means such as air or tap water outside the apparatus, or after being cooled by water and subjected to heat exchange and dehumidification, and then returned to the heating means.

  In general, in order to shorten the drying time of the laundry, for example, it is conceivable to increase the heat capacity of a heating means such as a heater, but the power consumption increases proportionally.

  Further, when heat exchange dehumidification with cooling water is used, a large amount of water is used, and the amount of water consumption increases in proportion to the drying time.

  Therefore, for example, in Japanese Patent Laid-Open No. 60-220097 (Patent Document 2), in order to reduce the power consumption and the amount of water used, a condenser ( A drying method has also been proposed in which an evaporator (corresponding to the cooling and dehumidifying means described above) and an evaporator (corresponding to the cooling and dehumidifying means described above) are provided to effectively use heat and cold. According to this drying method using a heat pump, air can be heated and cooled and dehumidified without using a heater or water, so that power consumption can be reduced and water can be saved.

  Japanese Patent Application Laid-Open No. 2004-215543 (Patent Document 3) and Japanese Patent Application Laid-Open No. 2005-40316 (Patent Document 4) circulate by exhausting circulating air in an air circulation path used for drying clothes. A clothes dryer and a dryer with a washing function using a heat pump are described which prevent the amount of heat of air from increasing and stabilize in a safe state.

  Japanese Patent Laying-Open No. 2006-212117 (Patent Document 5) describes a clothes drying apparatus that continues the operation of a compressor when a drying operation is interrupted in a clothes dryer using a heat pump. Japanese Patent Laying-Open No. 2006-61353 (Patent Document 6) describes a clothes drying apparatus using a heat pump that stops the operation of the compressor for a predetermined time after the drying operation is interrupted. Has been. By doing in this way, when the drying operation and the interruption of the drying operation are repeated in a short time, the burden on the compressor is reduced, and the return of the hot air temperature by the heat pump device is accelerated.

In Japanese Patent Application Laid-Open No. 2006-272024 (Patent Document 7) and Japanese Patent Application Laid-Open No. 2005-261703 (Patent Document 8), before starting the drying process, the operation of the compressor is started in advance and the drying process is started. A washing and drying machine using a heat pump is described which reduces the time.
JP 63-122500 A Japanese Unexamined Patent Publication No. 60-220097 JP-A-2004-215543 JP 2005-40316 A JP 2006-212117 A JP 2006-61353 A JP 2006-272024 A JP 2005-261703 A

  However, even with a drying method using a heat pump, since a compression means such as a compressor is newly used to compress the refrigerant, there is a problem that noise and vibration are generated during operation and noise during drying is increased. In addition, depending on the type of refrigerant used in the compressor, there arises a problem that the cost after disposal is high. In addition, from the perspective of preventing global warming, it is increasingly necessary to reduce the power consumption of electrical products in the future, and dryers and washing dryers are required to improve drying functions and reduce power consumption. .

  In addition, when a heat pump is used in the dryer, the amount of heat of the circulating air is increased by driving the heat pump, the temperature of the refrigerant of the heat pump is increased, and the temperature of the refrigerant is increased and the pressure is increased. Although it is possible to control the output of the heat pump by inverter control or the like, it is extremely difficult to significantly reduce the output, and it is difficult to reduce the amount of heat applied even when the amount of heat of the circulating air is excessive. Moreover, in order to compress and liquefy the high temperature and high pressure refrigerant | coolant, the burden concerning a heat pump becomes large. Therefore, the dryers described in Japanese Patent Application Laid-Open No. 2004-215543 (Patent Document 3) and Japanese Patent Application Laid-Open No. 2005-40316 (Patent Document 4) exhaust the circulated air whose amount of heat has increased to the outside. Unnecessary heat generated by the heat pump or steam contained in the circulating air may be discharged into the room where the dryer is installed, resulting in an increase in the amount of heat in the whole room or condensation due to the discharged steam. is there.

  In clothes dryers that use heat pumps, it takes a certain amount of time for the refrigerant pressure in the piping to reach an equilibrium state when the drying operation is interrupted and for the refrigerant to vaporize and liquefy when the drying operation is resumed. . Therefore, when the drying operation is resumed in a short time after the interruption of the drying operation, the drying operation is interrupted as in the clothes dryer described in JP 2006-212117 A (Patent Document 5). Nevertheless, it is necessary to continue driving the compressor, which consumes unnecessary power and places a heavy burden on the compressor. On the other hand, when the drying operation is interrupted as in the clothes dryer described in Japanese Patent Application Laid-Open No. 2006-61353 (Patent Document 6), if the compressor is not operated thereafter for a certain period of time, the drying operation is performed. The drying operation cannot be resumed in a short time after the interruption.

  Moreover, like the washing dryer described in JP 2006-272024 A (Patent Document 7) and JP 2005-261703 A (Patent Document 8), the compressor is operated in advance before entering the drying process. This causes unnecessary heat and noise, and increases the power consumption.

  Accordingly, an object of the present invention is to provide an efficient heating and dehumidifying device with less noise.

  A heating and dehumidifying device according to the present invention includes a first air path and a second air path for circulating gas, and a first heat exchange unit for heating the gas flowing through the first air path. A second heat exchanging part for cooling the gas flowing through the second air passage, and a Stirling engine including a heat generating head and an endothermic head, the first heat exchanging part being a heat generating head of the Stirling engine The heat exchange is performed so as to heat the gas, and the second heat exchange unit performs the heat exchange so that the gas is cooled by the heat absorption head of the Stirling engine.

  Conventionally, in a heat pump used in a heat dehumidifying apparatus, heat exchange is performed between a condensing unit that compresses a refrigerant by a compressor to change from gas to liquid and an evaporation unit that expands the refrigerant to change from liquid to gas. ing. That is, in the heat pump, the refrigerant moves from the condensing unit through the pipe or the like to the evaporating unit, changes from liquid to gas, and moves from the evaporating unit through the pipe or the like to the condensing unit to change from gas to liquid. It is necessary to repeat changing.

  On the other hand, the Stirling engine reciprocates the displacer in the cylinder, thereby compressing the working gas such as helium in the compression space to heat the heat generating head and expand the heat generating head to cool the heat absorbing head. As described above, in the Stirling engine, the working gas remains in a gaseous state and moves only between the compression space and the expansion space. The compression space and the expansion space are disposed at both ends of one cylinder, for example. In this case, the working gas reciprocates from one end of the cylinder to the other end while maintaining the gaseous state. .

  As described above, in the Stirling engine, the moving distance of the working gas is short, and it is not necessary to change the state of the refrigerant between the gas and the liquid. Therefore, the responsiveness of the Stirling engine is higher than that of the heat pump. For example, the time required from the start of driving the Stirling engine until the heat generating head and the heat absorbing head reach a predetermined temperature, the evaporation unit and the condensing unit are set to a predetermined temperature after starting the heat pump. It is shorter than the time required to become.

  Therefore, by using a Stirling engine, it is not necessary to start up for a long time before the start of the drying operation or at the start of the drying operation. Therefore, the controllability is higher than that of the heat pump, and energy saving, that is, energy consumption is effectively reduced. Thus, it is possible to obtain a heating and dehumidifying device that facilitates energy saving. As described above, the heating and dehumidifying device including the Stirling engine can shorten the time required to start the heating and dehumidifying device, and is required when the operation is once interrupted and then restarted during the operation of the heating and dehumidifying device. Time can be shortened.

  Further, the vibration system of the heat pump used in the conventional heat dehumidifying apparatus is a complicated vibration system including rotation vibration because a compressor is used for compression and expansion of the refrigerant. On the other hand, a Stirling engine has a simple vibration system compared to a heat pump. That is, in the Stirling engine, only a linear motion of reciprocation of the displacer is performed.

  Thus, since the Stirling engine has a simple vibration system, it is easy to absorb vibration. For example, the vibration can be easily suppressed by providing a vibration absorbing member such as a spring having the co-frequency of the displacer as the natural frequency. In a Stirling engine, vibration can be easily suppressed, so that noise due to vibration is less likely to occur.

  In this way, vibration and noise can be reduced, and usability, ie easy to use, energy saving, ie consumption, does not deteriorate the indoor environment where the dryer is installed. It is possible to provide a heating and dehumidifying device that can effectively reduce energy and facilitate energy saving.

  The heating and dehumidifying device according to the present invention includes a circulation path for allowing gas to flow from the second air path into the first air path, and the gas in the second air path is in the second heat exchange section. It is preferably cooled, flows into the first air passage through the circulation path, and is heated in the first heat exchange section.

  Thus, the gas that has flowed into the second air passage is cooled in the second heat exchange section, flows into the first air passage through the circulation path, and is heated in the first heat exchange section. Therefore, it can dehumidify efficiently.

  In the heating and dehumidifying apparatus according to the present invention, it is preferable that the heat generating head is disposed in the first air path to constitute the first heat exchange unit.

  This eliminates the need for a heat transfer path between the heat generating head and the first heat exchanging section, and wastes heat in the path between the heat generating head and the first heat exchanging section. Can be prevented.

  In the heating and dehumidifying device according to the present invention, it is preferable that the first heat exchange unit includes a fin disposed so as to contact the heat generating head.

  By doing in this way, gas can be efficiently heat-exchanged in a fin. In addition, the heat dehumidifying device can be reduced in size.

  In the heating and dehumidifying device according to the present invention, the first heat exchanging unit includes a heating unit for heating the gas and a heat conduction medium through which a heat conduction medium for conducting the heat of the heating head to the heating unit flows. It is preferable to have a flow path.

  By doing in this way, it becomes easy to optimize the position and shape of a 1st heat exchange part according to the shape of an air path, etc.

  In the heating and dehumidifying apparatus according to the present invention, it is preferable that the heat absorbing head is disposed in the second air passage to constitute the second heat exchange unit.

  This eliminates the need for a path for transmitting cold air between the heat absorbing head and the second heat exchange unit, and wastes cold air in the path between the heat absorbing head and the second heat exchange unit. Can be prevented.

  In the heating and dehumidifying device according to the present invention, it is preferable that the second heat exchange part includes a fin disposed so as to contact the heat absorbing head.

  By doing in this way, gas can be efficiently heat-exchanged in a fin. In addition, the heat dehumidifying device can be reduced in size.

In the heating and dehumidifying device according to the present invention, the second heat exchanging unit includes a cooling unit for cooling the gas and a heat conduction medium through which a heat conduction medium for conducting the heat of the heat absorbing head to the cooling unit flows. It is preferable to have a flow path.

  By doing in this way, it becomes easy to optimize the position and shape of a 2nd heat exchange part according to the shape of an air path, etc.

  The heating and dehumidifying device according to the present invention includes a connecting pipe disposed between the heat generating head and the heat absorbing head, and the heat generating head is disposed in the first air passage to constitute the first heat exchange unit. The heat absorbing head is disposed in the second air passage to form a second heat exchange unit, and a connection pipe is provided between the heat generating head and the heat absorbing head, and is connected to the heat generating head and the heat absorbing head. The pipes are arranged coaxially, and it is preferable to arrange the heat generating head, the heat absorbing head, and the connecting pipe in the circulation path.

  By doing so, the circulation path can be shortened to suppress the pressure deficit, and the thermal influence between the heat generating head and the heat absorbing head can be reduced by the air layer around the connecting pipe.

  As described above, according to the present invention, it is possible to provide an efficient heating and dehumidifying device with less noise.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(Embodiment 1-1)
FIG. 1 is a perspective view schematically showing the overall appearance of a washing / drying machine provided with the heating / dehumidifying device of the present invention as Embodiment 1-1 of this invention, and FIG. 2 is a washing / drying machine of FIG. It is a sectional side view which shows roughly the cross section which looked at the II-II line | wire direction.

  As shown in FIGS. 1 and 2, the washing and drying machine 200 includes a main body 210, a water tank 220 attached to the inside of the main body 210, and a water tank 220 as a container for storing laundry as an object to be dried. And a rotating drum 230 supported rotatably inside.

  An outer door 201 is attached to the front surface of the main body 210. An inner door 203 is attached inside the outer door 201. By opening the outer door 201 and opening the inner door 203, the laundry can be put into or taken out of the rotating drum 230 through the laundry inserting port 202 provided on the front surface of the main body 210. The laundry input port 202 can be closed by closing and closing the outer door 201. The inner door 203 has a central portion made of transparent glass so that the inside of the rotary drum 230 can be visually recognized, and has a recessed bowl shape, a so-called basin shape. A door packing 204 made of an elastic material such as rubber is fitted and fixed to the peripheral wall of the water tub 220 on the laundry input port 202 side. When the inner door 203 is closed, the door packing 204 is in close contact with the peripheral edge of the inner door 203 so that the water tank 220 is sealed.

The rotating drum 230 is supported so as to rotate around the shaft portion 231 inside the water tank 220. In this way, the drum type washing and drying machine 200 has a double structure composed of the water tank 220 and the rotating drum 230. The rotary drum 230 includes a drum body 232 that forms an inner peripheral wall surface at the center in the rotation axis direction, a drum lid 233 that forms an opening at one end, and a drum bottom 234 that forms an inner bottom wall surface at the other end. Are generally made from stainless steel sheet. An uneven surface such as a rib is formed on the drum bottom 234 by pressing to attach a structural component such as the shaft portion 231 and support a desired load, thereby improving the strength of the bottom wall surface. A large number of small holes 235 for water supply, drainage, and ventilation are provided in the peripheral wall and bottom of the rotary drum 230. A fluid balancer 205 is fixed to the outer peripheral edge of the drum lid 233 to prevent vibration during rotation. The shaft portion 231 includes a shaft of a drum rotation drive motor 236 for rotating the rotary drum 230. The rotation of the drum rotation drive motor 236 is controlled by an inverter circuit. The water tank 220 is elastically supported by a coil spring (not shown) from the upper part and by an anti-vibration damper (not shown) from the lower part. A water supply path 209 connected to tap water is disposed above the water tank 220, and is connected to the water tank 220 via the detergent case 207. A water supply valve 208 is provided in the middle of the water supply path 209 , and the supply from the tap water to the water tank 220 is controlled by opening and closing the water supply valve 208. A drain valve 206 is provided at the bottom of the water tank 220, and washing liquid and the like can be drained from the water tank 220 to the outside of the main body 210 by opening and closing the drain valve 206.

  FIG. 3 is a cross-sectional view showing the entire cross section of the Stirling engine.

  As shown in FIG. 3, the cylinders 110 and 111 are central to the assembly of the Stirling engine 100. The axes of the cylinders 110 and 111 are aligned on the same line. A piston 112 is inserted into the cylinder 110, and a displacer 113 is inserted into the cylinder 111. The piston 112 and the displacer 113 reciprocate without contacting the inner surfaces of the cylinders 110 and 111 by the gas bearing mechanism during operation of the Stirling engine 100. The piston 112 and the displacer 113 move with a predetermined phase difference.

  A cup-shaped magnet holder 114 is provided at one end of the piston 112. A displacer rod 115 projects from one end of the displacer 113. The displacer rod 115 passes through the piston 112 and the magnet holder 114 so as to freely slide in the axial direction.

  The cylinder 110 holds the linear motor 120 outside the portion corresponding to the operation area of the piston 112. The linear motor 120 includes an outer yoke 122 having a coil 121, an inner yoke 123 provided so as to be in contact with the outer peripheral surface of the cylinder 110, and a ring shape inserted into an annular space between the outer yoke 122 and the inner yoke 123. Magnet 124 and synthetic resin end brackets 125 and 126 for holding the outer yoke 122 and the inner yoke 123 in a predetermined positional relationship. The magnet 124 is fixed to the magnet holder 114.

  The central portion of the spring 130 is fixed to the hub portion of the magnet holder 114. The center portion of the spring 131 is fixed to the displacer rod 115. The outer peripheral portions of the springs 130 and 131 are fixed to the end bracket 126. A spacer 132 is disposed between the outer peripheries of the springs 130 and 131, whereby the springs 130 and 131 maintain a certain distance. The springs 130 and 131 are obtained by making a spiral cut into a disk-shaped material, and cause the displacer 113 to resonate with a predetermined phase difference (ideally about 90 ° phase difference) with respect to the piston 112. Play a role.

  A heat generating head 140 and a heat absorbing head 141 are arranged outside the portion of the cylinder 111 that corresponds to the operating region of the displacer 113. The heat generating head 140 has a ring shape and the heat absorbing head 141 has a cap shape, both of which are made of a metal having good heat conductivity such as copper or a copper alloy. The heat generating head 140 and the heat absorbing head 141 are supported outside the cylinder 111 with ring-shaped internal heat exchangers 142 and 143 interposed therebetween. Each of the internal heat exchangers 142 and 143 has air permeability, and transmits heat of the working gas passing through the inside to the heat generating head 140 and the heat absorbing head 141.

  A space surrounded by the heat generating head 140, the cylinders 110 and 111, the piston 112, the displacer 113, and the internal heat exchanger 142 becomes a compression space 145. A space surrounded by the heat absorbing head 141, the cylinder 111, the displacer 113, and the internal heat exchanger 143 becomes an expansion space 146.

  A regenerator 147 is disposed between the internal heat exchangers 142 and 143. The regenerator 147 is obtained by winding a resin film into a cylindrical shape, and a plurality of minute protrusions are scattered on one side of the film to form a gap corresponding to the height of the protrusion between the films. It is said. A regenerator tube 148 wraps the outside of the regenerator 147 and forms an airtight passage between the heat generating head 140 and the heat absorbing head 141. The heat generating head 140, the regenerator tube 148, and the heat absorbing head 141 are arranged coaxially. The regenerator tube 148 is an example of a connecting tube.

  A cylindrical pressure vessel 150 wraps the linear motor 120, the cylinder 110, and the piston 112. The inside of the pressure vessel 150 becomes a back pressure space 151. On the peripheral surface of the pressure vessel 150, a terminal portion 152 for supplying electric power to the linear motor 120 and a pipe 153 for enclosing a working gas therein are arranged.

A dynamic vibration absorber 160 is attached to the outer surface of the pressure vessel 150. The dynamic vibration absorber 160 includes a shaft 161 protruding from the center of the end face of the pressure vessel 150, a plate-like spring 162 fixed at the center to the shaft 161, and a mass (mass) 163 disposed on the periphery of the spring 162. The spring 162 is a stack of a plurality of thin plate springs.

  The Stirling engine 100 operates as follows. A magnetic field penetrating the magnet 124 is generated between the outer yoke 122 and the inner yoke 123 that supply an alternating current to the coil 121 of the linear motor 120, and the magnet 124 reciprocates in the axial direction. By supplying power with a frequency that matches the resonance frequency determined by the total mass of the piston system (piston 112, magnet holder 114, magnet 124, and spring 130) and the spring constant of the spring 130, the piston system has a smooth sine. Start wavy reciprocating motion.

  In the displacer system (the displacer 113, the displacer rod 115, and the spring 131), the resonance frequency determined by the total mass and the spring constant of the spring 131 is set to match the driving frequency of the piston 112.

  By the reciprocating motion of the piston 112, compression and expansion are repeated in the compression space 145. As the pressure changes, the displacer 113 also reciprocates. At this time, there is a phase difference between the displacer 113 and the piston 112 due to flow resistance between the compression space 145 and the expansion space 146. In this way, the displacer 113 having a free piston structure reciprocates in synchronization with the piston 112 with a predetermined phase difference.

  With the above operation, a Stirling cycle is formed between the compression space 145 and the expansion space 146. In the compression space 145, the temperature of the working gas increases based on the isothermal compression change, and in the expansion space 146, the temperature of the working gas decreases based on the isothermal expansion change. For this reason, the temperature of the compression space 145 rises and the temperature of the expansion space 146 falls.

  The working gas that moves back and forth between the compression space 145 and the expansion space 146 during operation passes through the internal heat exchangers 142 and 143 to transmit the heat it has to the heating head 140 and the heat absorption head 141. Since the working gas flowing from the compression space 145 into the regenerator 147 has a high temperature, the heat generating head 140 is heated. Since the working gas flowing from the expansion space 146 into the regenerator 147 has a low temperature, the heat absorbing head 141 is cooled.

  The regenerator 147 functions to pass only the working gas without transferring the heat of the compression space 145 and the expansion space 146 to the space on the other side. The hot working gas that has entered the regenerator 147 from the compression space 145 through the internal heat exchanger 142 gives the heat to the regenerator 147 when passing through the regenerator 147, and enters the expansion space 146 when the temperature is lowered. Inflow. The low-temperature working gas that has entered the regenerator 147 from the expansion space 146 through the internal heat exchanger 143 recovers heat from the regenerator 147 when passing through the regenerator 147, and enters the compression space 145 in a state where the temperature has risen. Inflow. That is, the regenerator 147 serves as a heat storage means.

  When the piston 112 and the displacer 113 reciprocate, vibration occurs in the Stirling engine 100, and the dynamic vibration absorber 160 suppresses this vibration.

  FIG. 4 is a perspective view showing the entire body of the heat dehumidifying apparatus.

  As shown in FIG. 4, the main body of the heating and dehumidifying apparatus 400 includes a Stirling engine 410, a high-temperature side heat exchange unit 420 as a first heat exchange unit, and a low-temperature side heat exchange unit 430 as a second heat exchange unit. Prepare. The Stirling engine 410 includes a heat generating head 411 and a heat absorbing head 412. The configuration and operation of the Stirling engine 410 are the same as those of the Stirling engine 100 shown in FIG. The high temperature side heat exchange unit 420 includes heating fins 421 connected to the heat generating head 411 as fins, and the low temperature side heat exchange unit 430 includes cooling fins 431 connected to the heat absorbing head 412 as fins. The heating fins 421 and the cooling fins 431 have a disk shape, and the central portions are directly connected to the heat generating head 411 and the heat absorbing head 412, respectively. The cooling fins 431, the heating fins 421, and the Stirling engine 410 are arranged so as to be aligned substantially in a straight line, and are integrated to constitute the main body of the heating and dehumidifying device 400. The heating and dehumidifying device 400 includes this main body, a warm air side path portion and a humid air side path portion shown in FIG.

  As described above, in the heat dehumidifying apparatus 400, the high temperature side heat exchanging unit 420 includes the heating fins 421 disposed so as to be in contact with the heat generating head 411, and the low temperature side heat exchanging unit 430 is in contact with the heat absorbing head 412. Cooling fins 431 arranged as described above.

  By doing in this way, heat can be efficiently exchanged between the gas in the heating fins 421 and the cooling fins 431. Moreover, the heat dehumidifying apparatus 400 can be reduced in size.

  FIG. 5 is a cross-sectional view showing an outline when the washing / drying machine is viewed from the direction of the line V-V in FIG. 2.

  As shown in FIGS. 2 and 5, in the main body 210 of the washing / drying machine 200, a hot air path portion 241 and a wet air path portion 242 are arranged on the back side of the rotary drum 230. The hot air path portion 241 and the wet air path portion 242 communicate with the inside of the water tank 220 through an intake port 245 and an exhaust port 246, respectively. The hot air path portion 241 and the wet air path portion 242 are connected via a circulation path portion 243 extending substantially linearly below the water tank 220. The main body of the heating / dehumidifying device 400 is provided in the circulation path part 243 such that the cooling fins 431 are on the wet air path part 242 side and the heating fins 421 are on the hot air path part 241 side. Below the water tank 220, a blower mechanism unit 244 is disposed inside the wet air passage unit 242.

As shown in FIG. 2, a hot water path portion 247 in the water tank is provided between the inner peripheral wall surface of the water tank 220 and the outer peripheral wall surface of the drum body 232 of the rotating drum 230. Further, the inner peripheral wall surface of the water tank 220, the drum body 232 and the drum bottom 234 of the rotating drum 230 form a water tank inside humid air passage portion 248. An intake port and an exhaust port are provided below the water tank 220. In addition, an exhaust port and an intake port may be provided in a front part, a side surface, or an upper part. As shown in FIG. 5, the exhaust port is connected to the circulation path part 243 via a wet air path part 242 provided outside the back surface of the water tank 220. A blower mechanism unit is disposed in the wet air path unit 242. A main body of the heating and dehumidifying device 400 including a Stirling engine is disposed in the circulation path portion 243 extending substantially linearly. More specifically, the heat generating head 411, the heat absorbing head 412, and the regenerator tube 148 of the main body of the heat dehumidifying apparatus 400 are disposed in the circulation path portion 243. The circulation path part 243 is connected to the intake port via a hot air path part 241 provided outside the back surface of the water tank 220. The arrow of the dashed-two dotted line in FIG. 2 shows the direction through which a wind flows. In addition, the path | route to the high temperature side heat exchange part 420 of the warm air path | route part 247, the warm air path | route part 241, and the circulation path | route part 243 in a water tank is an example of a 1st air path, the wet air path | route part 248 in a water tank, a humid air path | route The path to the low temperature side heat exchange unit 430 of the part 242 and the circulation path unit 243 is an example of a second air path, the path to the high temperature side heat exchange unit 420 of the circulation path unit 243 and the path to the low temperature side heat exchange unit 430 The path between is an example of a circulation path.

  Hereinafter, the washing process, the rinsing process, the dehydrating process, and the drying process performed using the washing / drying machine 200 configured as described above will be described in the order of steps.

First, the outer door 201 and the inner door 203 are opened, and after the laundry is loaded from the laundry loading port 202, the inner door 203 and the outer door 201 are closed. Put the detergent in the detergent case and operate the operation panel. Thereby, the outer door 201 and the inner door 203 are locked, the water supply valve 208 is opened, and water is supplied to the water tank 220 through the water supply path 209 and the detergent case 207. When a water level sensor (not shown) detects that the water level in the water tank 220 has reached a predetermined value, the water supply valve 208 is closed, and the rotating drum 230 is rotated by the drum rotation drive motor 236 according to the rotation chart for the washing process. Is done. In this way, the washing process is started.

  In addition, regarding the rotation chart of the rotating drum 230, the rotation speed, the rotation cycle, the reversal cycle, and the like are different for each of the washing process, the rinsing process, the dehydration process, and the drying process, or depending on the type and course of the laundry. The rotation chart is preset. The rotation chart is selected by the user or programmed to be selected automatically.

    When the washing process is finished, the drain valve 206 is opened and the washing liquid is discharged out of the main body. When the drainage is completed, an intermediate dewatering process is performed in which the rotary drum 230 is rotated at a high speed on the rotation chart for the intermediate dewatering process. In the intermediate dehydration process, the washing liquid contained in the laundry is discharged to the inner wall surface of the water tank 220 through the small holes 235 provided in the peripheral wall of the rotating drum 230 by the centrifugal force generated by the high-speed rotation of the rotating drum 230. The washing liquid flows down along the inner wall surface of the water tank 220 and is discharged out of the main body through the drain valve 206.

  When the intermediate dehydration process is completed, the program proceeds to the rinsing process. After the drain valve 206 is closed, the water supply valve 208 is opened, and water is supplied to the water tank 220 through the detergent case. When a water level sensor (not shown) detects that the water level in the water tank 220 has reached a predetermined value, the water supply valve 208 is closed and the rotating drum 230 is rotated by the drum rotation drive motor 236 according to the rotation chart for the rinsing process. Is done. After the intermediate dehydration step and the rinsing step are repeated a plurality of times, the process proceeds to the final rinsing step. In the final rinsing step, the water supply valve 208 is opened, and water containing a softening finish is supplied to the water tank 220.

  When the final rinsing process is completed, the drain valve 206 is opened and the rinsing liquid is discharged out of the main body 210. When the drainage is completed, a final dewatering process is performed in which the rotating drum 230 is rotated at high speed according to the rotation chart for the final dewatering process. In the final dewatering step, the rinsing liquid contained in the laundry is discharged to the inner wall surface of the water tank 220 through the small holes 235 provided in the peripheral wall of the rotating drum 230 by the centrifugal force generated by the high-speed rotation of the rotating drum 230 as in the intermediate dewatering step. Is done.

  When the final dehydration process is completed, the process proceeds to the drying process. In the drying process, the rotating drum 230 is rotated, and the heating and dehumidifying device 400 and the air blowing mechanism unit 244 are driven.

  When the Stirling engine 410 of the heating and dehumidifying device 400 is driven, heat is exchanged so that the gas is heated in the heating fins 421, and heat is exchanged so that the gas is cooled in the cooling fins 431.

  By driving the heating / dehumidifying device 400 and the air blowing mechanism 244, the gas heated by the heating fin 421 flows through the hot air path 241 as indicated by the two-dot chain line arrow in FIG. It flows into the inside of the water tank 220 through the hot air path part 247 in the water tank from 245 and blows into the rotating drum 230 (FIG. 2) disposed inside the water tank 220. The gas comes into contact with the laundry in the rotating drum 230 (FIG. 2), then flows out of the rotating drum 230 through the small hole 235, and passes through the exhaust port 246 formed in the lower part of the water tank 220. Exhaust into the humid air passage 242. The gas exhausted to the wet air passage portion 242 has high humidity due to moisture contained in the laundry in the rotating drum 230. The gas containing moisture flows as indicated by the one-dot chain line arrow in FIG. 5, returns to the cooling fin 431, is cooled by the cooling fin 431, and is dehumidified. The moisture removed from the gas is discharged from the main body 210 through the drain pipe (not shown) from below the cooling fins 431. The dehumidified gas returns to the heating fin 421 through the circulation path 243. A drying process is performed by repeating this cycle.

  As described above, the washing / drying machine 200 flows out the gas from the rotary drum 230 for storing the laundry, the hot air path portion 241 for allowing the gas to flow into the rotary drum 230, and the rotary drum 230. A hot air path section 242 for heating, a high temperature side heat exchange section 420 for heating the gas flowing through the hot air path section 241, and a low temperature side heat exchange for cooling the gas flowing through the wet air path section 242 Unit 430, and a Stirling engine 410 including a heat generating head 411 and a heat absorbing head 412. The high temperature side heat exchanging unit 420 performs heat exchange so as to heat the gas with the heat generating head 411 of the Stirling engine 410, and the low temperature side The heat exchanging unit 430 performs heat exchange so that the heat is absorbed by the heat absorbing head 412 of the Stirling engine 410.

  Conventionally, in a heat pump used in a dryer, heat is exchanged between a condensing unit that compresses a refrigerant by a compressor to change from gas to liquid and an evaporation unit that expands the refrigerant to change from liquid to gas. Yes. That is, in the heat pump, the refrigerant moves from the condensing unit through the pipe or the like to the evaporating unit, changes from liquid to gas, and moves from the evaporating unit through the pipe or the like to the condensing unit to change from gas to liquid. It is necessary to repeat changing.

  On the other hand, the Stirling engine reciprocates the displacer in the cylinder, thereby compressing the working gas such as helium in the compression space to heat the heat generating head and expand the heat generating head to cool the heat absorbing head. As described above, in the Stirling engine, the working gas remains in a gaseous state and moves only between the compression space and the expansion space. The compression space and the expansion space are disposed at both ends of one cylinder, for example. In this case, the working gas reciprocates from one end of the cylinder to the other end while maintaining the gaseous state. .

  Thus, in the Stirling engine, since it is not necessary to change the state of the refrigerant between the gas and the liquid, the responsiveness of the Stirling engine is higher than that of the heat pump. For example, the time required from the start of driving the Stirling engine until the heat generating head and the heat absorbing head reach a predetermined temperature, the evaporation unit and the condensing unit are set to a predetermined temperature after starting the heat pump. It is shorter than the time required to become.

  Therefore, by using a Stirling engine, a start-up operation for a long time is unnecessary before starting the drying operation or at the start of the drying operation, so the controllability is higher than the heat pump, and energy saving, that is, it is easy to reduce energy consumption, A dryer that facilitates energy saving is obtained. Thus, a dryer equipped with a Stirling engine can shorten the time required to start the dryer, and, like a heat pump, it is necessary to wait for the time until the refrigerant becomes a uniform gas from the mixture of gas and liquid. Therefore, once the operation is interrupted during the operation of the dryer, the time required for starting again can be shortened.

  Further, the vibration system of the heat pump used in the conventional heat dehumidifying apparatus is a complicated vibration system including rotation vibration because a compressor is used for compression and expansion of the refrigerant. On the other hand, a Stirling engine has a simple vibration system compared to a heat pump. That is, in the Stirling engine, only a linear motion of reciprocation of the displacer is performed.

  Thus, since the Stirling engine has a simple vibration system, it is easy to absorb vibration. For example, the vibration can be easily suppressed by providing a vibration absorbing member such as a spring having the co-frequency of the displacer as the natural frequency. In a Stirling engine, vibration can be easily suppressed, so that noise due to vibration is less likely to occur.

  By doing this, vibration and noise can be reduced, usability, i.e., easy to use, energy saving, i.e., energy consumption can be effectively reduced, and heat dehumidification device that facilitates energy saving. 400 can be provided.

The heating and dehumidifying device 400 includes a circulation path part 243 for allowing gas to flow from the wet air path part 242 to the hot air path part 241, and the gas is cooled in the low temperature side heat exchange part 430 and passes through the circulation path part 243. Then, it flows into the warm air path section 241 and is heated in the high temperature side heat exchanging section 420 .

In this way, the gas that has flowed out into the wet air path section 242 is cooled in the low temperature side heat exchange section 430, flows into the warm air path section 241 through the circulation path section 243, and is heated in the high temperature side heat exchange section 420 . Therefore, it can dehumidify efficiently.

  The washer / dryer 200 is disposed so as to cover the rotary drum 230 and includes a water tank 220 for containing water. The rotary drum 230 is rotatably supported in the water tank 220 and is accommodated in the rotary drum 230. The laundry to be performed can be washed in the rotating drum 230.

By doing in this way, it can dry quickly after completion | finish of washing. Further, in the Stirling engine 410 , the high temperature portion and the low temperature portion are not formed separately by being connected to the Stirling engine main body by piping or the like, and a compressor, an expansion valve, a high temperature portion (condensing portion), a low temperature portion necessary for the heat pump are not formed. Since there is no need for a pipe for circulating the refrigerant connecting to the (evaporating part) and the structure is simple, the pipe breaks even when the washing / drying machine 200, which is complex and easily generates large vibration during washing, vibrates. In addition, it is possible to provide a highly reliable washing / drying machine 200 that is less prone to malfunction.

  In the washing / drying machine 200, a regenerator tube 148 is provided between the heat generating head 411 and the heat absorbing head 412, and the heat generating head 411, the heat absorbing head 412 and the regenerator tube 148 are arranged coaxially. The heat absorption head 412 and the regenerator tube 148 are arranged in the circulation path.

  In this way, the circulation path can be shortened to suppress the pressure deficit, and the thermal effect of the heat generating head 411 and the heat absorbing head 412 on each other can be reduced by the air layer around the regenerator tube 148. be able to.

  In this embodiment, the heat dehumidifying apparatus is used for a washing dryer, but the heat dehumidifying apparatus of the present invention may be used for a tableware dryer, a tableware washing dryer, a dehumidifier, a bathroom dryer, or the like.

(Embodiment 1-2)
FIG. 6: is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing / drying machine is provided as Embodiment 1-2 of this invention.

As shown in FIG. 6, the heating and dehumidifying apparatus 500 includes a Stirling engine 510, a high-temperature side heat exchange unit 520 as a first heat exchange unit, and a low-temperature side heat exchange unit 530 as a second heat exchange unit. The Stirling engine 510 includes a heat generating head 511 and a heat absorbing head 512. The configuration and operation of the Stirling engine 510 are the same as those of the Stirling engine 100 shown in FIG. The high temperature side heat exchanging unit 520 includes a heating unit 522 for heating a gas, and a heat conduction medium channel 523 through which a heat conduction medium for conducting the heat of the heat generating head 511 to the heating unit 522 flows. The low temperature side heat exchanging unit 530 includes a cooling unit 532 for cooling the gas, and a heat conduction medium flow path 533 through which a heat conduction medium for conducting the heat of the heat absorbing head 512 to the cooling unit 532 flows. For example, water is used as the heat conduction medium. The heating unit 522 and the cooling unit 532 are both plate-shaped in this embodiment, but may be in other forms. Moreover, although the heat conductive medium flow path 523 and the heat conductive medium flow path 533 are tubular in this embodiment, other forms may be used. The heating and dehumidifying device 500 includes this main body, and a warm air side path portion and a humid air side path portion shown in FIG.

  As described above, in the heating and dehumidifying apparatus 500, the high temperature side heat exchanging unit 520 has a heating unit 522 for heating the gas and a heat conduction medium for conducting the heat of the heat generating head 511 to the heating unit 522. A heat transfer medium flow path 523. The low temperature side heat exchanging unit 530 includes a cooling unit 532 for cooling the gas, and a heat conduction medium channel 533 through which a heat conduction medium for conducting the heat of the heat absorbing head 512 to the cooling unit 532 flows. .

  By doing in this way, the position and shape of the high temperature side heat exchange part 520 and the low temperature side heat exchange part 530 are matched with the shape of the warm air path part 241 (FIG. 5) and the humid air path part 242 (FIG. 5). Optimization.

  Other configurations and effects of the washer-dryer 200 of Embodiment 1-2 are the same as those of Embodiment 1-1.

(Embodiment 1-3)
FIG. 7: is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing / drying machine is provided as Embodiment 1-3 of this invention.

  As shown in FIG. 7, the heating and dehumidifying apparatus 600 includes a Stirling engine 610, a high-temperature side heat exchange unit 620 as a first heat exchange unit, and a low-temperature side heat exchange unit 630 as a second heat exchange unit. The Stirling engine 610 includes a heat generating head 611 and a heat absorbing head 612. The configuration and operation of the Stirling engine 610 are the same as those of the Stirling engine 100 shown in FIG.

  The high temperature side heat exchanging unit 620 includes heating fins 621 connected to the heat generating head 611 as fins. The heating fin 621 has a disk shape, and the central portion is directly connected to the heat generating head 611.

The low temperature side heat exchanging unit 630 includes a cooling unit 632 for cooling the gas, and a heat conduction medium channel 633 for flowing a heat conduction medium for conducting the heat of the heat absorbing head 612 to the cooling unit 632. For example, water is used as the heat conduction medium. The cooling unit 632 has a plate shape in this embodiment, but may have other forms. In addition, the heat conduction medium flow path 633 is tubular in this embodiment, but may have other forms.

  The heating and dehumidifying device 600 includes this main body, and a warm air side path portion and a humid air side path portion shown in FIG.

  Thus, in the heat dehumidifying apparatus 600, the heat generating head 611 is arranged in the hot air path portion.

  By doing so, a path for transferring heat between the heat generating head 611 and the high temperature side heat exchanging part 620 becomes unnecessary, and heat is wasted in the path between the heat generating head 611 and the high temperature side heat exchanging part 620. Can be prevented from being consumed.

  In the heating and dehumidifying apparatus 600, the high temperature side heat exchanging unit 620 includes heating fins 621 arranged so as to be in contact with the heating head 611.

  By doing in this way, gas can be efficiently heat-exchanged in the heating fin 621. Moreover, the heat dehumidifying apparatus 600 can be reduced in size.

  In the heat dehumidifying apparatus 600, the low temperature side heat exchanging unit 630 includes a cooling unit 632 for cooling the gas and a heat conduction through which a heat conduction medium for conducting the heat of the heat absorbing head 612 to the cooling unit 632 flows. Medium flow path 633.

  By doing so, for example, it becomes easy to reduce the thermal effects exerted on each other by separating the heating head 611 and the heating fins 621 and the cooling unit 632 on the air path. Further, the position and shape of the cooling unit 632 such as the arrangement of the cooling unit 632 in the surplus space are optimized in accordance with the shape of the wet air passage unit 242 (FIG. 5) and the overall component arrangement of the washing / drying machine 200. It becomes easy.

  Other configurations and effects of the washer-dryer 200 of Embodiment 1-3 are the same as those of Embodiment 1-1.

(Embodiment 1-4)
FIG. 8: is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing / drying machine is provided as Embodiment 1-4 of this invention.

  As shown in FIG. 8, the heating and dehumidifying device 700 includes a Stirling engine 710, a high-temperature side heat exchange unit 720 as a first heat exchange unit, and a low-temperature side heat exchange unit 730 as a second heat exchange unit. The Stirling engine 710 includes a heat generating head 711 and a heat absorbing head 712. The configuration and operation of the Stirling engine 710 are the same as those of the Stirling engine 100 shown in FIG.

  The high temperature side heat exchanging unit 720 includes a heating unit 722 for heating a gas, and a heat conduction medium flow path 723 for flowing a heat conduction medium for conducting the heat of the heat generating head 711 to the heating unit 722. . For example, water is used as the heat conduction medium. The heating unit 722 has a plate shape in this embodiment, but may have other forms. In addition, the heat conduction medium flow path 723 is tubular in this embodiment, but may have other forms.

  The low temperature side heat exchange part 730 has the cooling fin 731 connected to the heat absorption head 712 as a fin. The cooling fin 731 has a disk shape, and the central portion is directly connected to the heat absorbing head 712.

  The heating and dehumidifying device 700 includes this main body, and a warm air side path section and a humid air side path section shown in FIG.

  As described above, the heat dehumidifying apparatus 700 is configured such that the heat absorbing head 712 is disposed in the humid air path portion.

  By doing so, a path for transferring heat between the heat absorbing head 712 and the low temperature side heat exchanging unit 730 becomes unnecessary, and heat is wasted in the path between the heat absorbing head 712 and the low temperature side heat exchanging unit 730. It is possible to prevent consumption.

  As described above, in the heating and dehumidifying apparatus 700, the low temperature side heat exchanging unit 730 includes the cooling fins 731 disposed so as to be in contact with the heat absorbing head 712.

  By doing in this way, heat can be efficiently exchanged in the cooling fins 731. Moreover, the heat dehumidifying apparatus 700 can be reduced in size.

  In the heating and dehumidifying apparatus 700, the high temperature side heat exchanging unit 720 includes a heating unit 722 for heating a gas and a heat conduction medium flow through which a heat conduction medium for conducting the heat of the heating head 711 to the heating unit 722 flows. Path 723.

  By doing so, for example, it becomes easy to reduce the thermal influence exerted on each other by separating the distance on the air path between the heating unit 722, the heat absorbing head 712, and the cooling fin 731. Further, the position and shape of the heating unit 722 such as the arrangement of the heating unit 722 in the surplus space are optimally matched to the shape of the warm air path unit 241 (FIG. 5) and the overall component arrangement of the washing / drying machine 200. It becomes easy to make.

  Other configurations and effects of the washer-dryer 200 of Embodiment 1-4 are the same as those of Embodiment 1-1.

Embodiment 1-5
FIG. 9 is a side sectional view schematically showing a side section of a washing / drying machine provided with the heating / dehumidifying device of the present invention as Embodiment 1-5 of the present invention, and FIG. 10 is a view of the washing / drying machine from the back side. FIG.

  As shown in FIGS. 9 and 10, the washing / drying machine 300 includes a main body 310, a water tank 320 attached to the inside of the main body 310, and a container for storing laundry as an object to be dried. A rotating drum 330 rotatably supported inside.

  An outer door 301 is attached to the upper surface of the main body 310. By opening the outer door 301, the laundry is put into the rotating drum 330 through the loading slot 302 (not shown) provided in the water tub 320 and the rotating drum 330 or rotated from the laundry loading port 302 provided on the upper surface of the main body 310. The laundry 330 can be taken out from the drum 330 and the laundry input port 302 can be closed by closing the outer door 301.

  The rotating drum 330 is supported inside the water tank 320 so as to rotate around a shaft portion 331 extending substantially horizontally. In this way, the drum type washing and drying machine 300 has a double structure constituted by the water tank 320 and the rotating drum 330. The shaft portion 331 is disposed on each of the left and right sides of the rotating drum 330 and includes a shaft of a drum rotation driving motor 336 for rotating the rotating drum 330. Note that the drum rotation drive motor may be provided only on one side as long as a desired driving force can be obtained.

  The inner peripheral wall surface of the water tank 320 and the outer peripheral wall surface of the rotating drum 330 form a warm air path part 341 as a first air path and a wet air path part 342 as a second air path. An intake port 345 and an exhaust port 346 are provided below the water tank 320. The intake port 345 and the exhaust port 346 may be provided in the upper part or the side part. The exhaust port 346 and the intake port 345 are connected via a circulation path part 343 as a circulation path outside the water tank 320. In the circulation path part 343, a heat dehumidifying device 400 including a blower mechanism part 344 and a Stirling engine 410 is arranged.

  Inside the main body 310 of the washing / drying machine 300, a hot air path portion 341 and a wet air path portion 342 are arranged on the side surface side of the rotary drum 330. The warm air path portion 341 and the humid air path portion 342 communicate with the inside of the water tank 320 through the intake port 345 and the exhaust port 346, respectively. The hot air path unit 341 and the wet air path unit 342 are connected to each other below the water tank 320 via the circulation path unit 343. In the circulation path part 343 extending substantially linearly, the main body of the heating and dehumidifying device 400 is arranged such that the cooling fins 431 are disposed on the wet air path part 342 side and the heating fins 421 are disposed on the hot air path part 341 side. , Provided. Below the water tank 320, a blower mechanism part 344 is disposed inside the wet air path part 342.

  When the Stirling engine 410 of the heating and dehumidifying device 400 is driven, heat is exchanged so that the gas is heated in the heating fins 421, and heat is exchanged so that the gas is cooled in the cooling fins 431.

  By driving the heating and dehumidifying device 400 and the air blowing mechanism unit 344, the gas heated by the heating fin 421 flows through the hot air path unit 341 as indicated by the two-dot chain line arrow in the drawing, and the intake port 345 The water flows into the water tank 320 and blows into the rotating drum 330 disposed inside the water tank 320. After the gas contacts the laundry in the rotating drum 330, the gas flows out of the rotating drum 330 through a small hole, passes through the exhaust port 346 formed in the lower part of the water tank 320, and the wet air path portion 342. Exhausted. The gas exhausted to the wet air passage portion 342 has high humidity due to moisture contained in the laundry in the rotating drum 330. The gas containing moisture flows as indicated by the one-dot chain line arrow in the figure, returns to the cooling fin 431, is cooled by the cooling fin 431, and is dehumidified. The moisture removed from the gas is drained from the main body 310 from below the cooling fins 431 through a drain pipe (not shown). The dehumidified gas returns to the heating fin 421 through the circulation path portion 343. A drying process is performed by repeating this cycle.

  Other configurations and effects of the washing / drying machine 300 according to Embodiment 1-5 are the same as those of the washing / drying machine 200 according to Embodiment 1-1.

(Embodiment 2-1)
Hereinafter, Embodiment 2-1 of this invention is demonstrated using FIG. 11 and FIG. FIG. 11 is a cross-sectional view illustrating a configuration of a water supply / drainage path of a drum type washing / drying machine including a heating / dehumidifying device according to Embodiment 2-1 of the present invention, and FIG. 12 is a drum type according to Embodiment 2-1 of the present invention. It is sectional drawing which shows the structure of the drying ventilation path | route of a washing dryer.

  As shown in FIG. 11, a front opening 1a for taking in and out laundry is formed on the front surface of a substantially rectangular parallelepiped main body 1, and a door 2 for opening and closing the insertion opening 1a can be rotated by a hinge mechanism. Is provided. Inside the main body 1, a bottomed cylindrical water tank 3 having an opening 3 a facing the charging port 1 a at one end is slanted so that the opening 3 a side is higher with respect to the back surface thereof, The opening 3 a of the water tank 3 and the charging port 1 a of the main body 1 are connected in a watertight manner with a packing 4. The water tank 3 is swingably arranged by being supported by a support device such as a damper (not shown).

  A rotating tub 5 for storing laundry is rotatably provided in the water tub 3. The rotating tub 5 has a bottomed cylindrical shape having an opening 5a opposite to the opening 3a at one end in the rotation axis direction, and is inclined so that the opening 5a side is higher than the bottom surface (back surface). is doing. A fluid balancer 6 is provided on the periphery of the opening of the rotary tank 5, and a plurality of holes are provided in the peripheral wall of the rotary tank 5. In a state where the door 2 is rotated and the input port 1a is opened, the laundry is put into the rotary tub 5 and the laundry is taken out from the rotary tub 5 through the input port 1a, the opening 3a, and the opening 5a. Done.

  A rotating shaft 5b is fixed to the bottom surface (rear surface) of the rotating tub 5, and is rotatably supported by the water tub 3 via a bearing 5c so that the rotating shaft is inclined. A drum pulley 5d is attached to the end of the rotating shaft 5b opposite to the side on which the rotating tub is attached.

  A stepped portion in which the top surface of the main body 1 is partially lowered is provided at the upper back of the main body 1, and a water supply port 7 for introducing water from the water supply into the main body 1 is disposed on the stepped portion. A water supply valve (not shown) is arranged on the downstream side of the water supply port 7, and the water supply valve is opened and closed in accordance with instructions from a control device (not shown) that controls the operation of each part of the washing machine. Be controlled. When the water supply valve is opened by an instruction from the control device, water from the water supply is introduced into the main body 1 from the water supply port 7. The water that has passed through the water supply port 7 is supplied into the detergent case 9 through the water supply channel 8 and mixed with the detergent, and then supplied into the water tank 3 through the water supply pipe 10.

  Further, a drain pipe 11 that constitutes a discharge path for the water supplied into the water tank 3 to the outside of the main body 1 is connected to the lower side of the rear side of the water tank 3. Foreign matter such as yarn waste is removed from the water discharged from the water tank 3 to the drain pipe 11 by the drain filter 12a disposed in the filter device 12. The filter device 12 is provided with an air trap 12b, and one end of a pressure guiding tube 13 communicating with the inside of the air trap 12b is connected. A water level sensor 14 is connected to the other end of the pressure guiding tube 13, and when it is easy to wash, the water level in the water tank 3 is detected by measuring the air pressure in the air trap 12 b with the water level sensor 14. . The water from which foreign matter has been removed by the filter device 12 flows into the drainage channel 15. A drain valve 16 is arranged on the downstream side of the drain passage 15, and the drain valve 16 is opened and closed in accordance with instructions from a control device (not shown) that controls the operation of each part of the washing machine, so that drainage from the inside of the main body 1 is performed. Be controlled. When the drain valve 16 is opened by an instruction from the control device, the water in the drain channel 15 is discharged out of the main body 1 through the drain hose 17. The drainage channel 15 and the drainage hose 17 are part of the drainage channel.

  As shown in FIG. 12, an installation base 18 is provided at the lower part of the water tank, and a motor 19 capable of controlling the rotation speed for rotating the rotary tank 5 is disposed on the installation base 18. A motor shaft 19 a is attached to the motor 19, and a motor pulley 20 is provided on the opposite side of the motor shaft 19 a to which the motor 19 is attached. The motor pulley 20 and the rotary tank pulley 5d are wound around the belt 21 so that the power of the motor pulley 20 can be transmitted to the rotary tank pulley 5d.

  A clutch mechanism 22 is inserted into the motor shaft 19a, and is configured to be able to switch between a state in which the rotational driving force of the motor shaft 19a is transmitted to a transmission mechanism portion 23 provided therebelow or a state in which it is not transmitted. Yes. The rotational driving force transmitted to the transmission mechanism unit 23 is supplied to the heat exchange unit 24 and used as power for the heat exchange unit 24. More detailed configurations and operations of the clutch mechanism 22, the transmission mechanism unit 23, and the heat exchange unit 24 will be described later.

  A ventilation path (circulation duct) 25 which is an example of a circulation duct through which air for drying the laundry put in the rotary tub 5 circulates is provided from the rear rear side to the lower part and front front of the water tank. In the ventilation path 25, a blower 26 and a heat exchange unit 24 that are airflow sources of the ventilation path 25 are arranged in the path. During the drying operation, the air in the water tank 3 is discharged to the ventilation path 25 through the exhaust port 25a. The air flowing into the ventilation path 25 is sent to the heat exchanging unit 24 by a blower 26 which is an example of a fan, cooled and dehumidified by a heat absorbing head 38a, which will be described later, and then heated by a heat generating head 38b. It is sent again to the water tank 3 from 25b. A part of the ventilation path 25 may be provided along the peripheral edge of the back surface of the water tank 3.

  Next, the structure of the clutch mechanism 22, the transmission mechanism part 23, and the heat exchange part 24 is demonstrated using FIGS. 13-15. 13 is an enlarged view of the main part of FIG. 12, FIG. 14 is an exploded perspective view of the clutch mechanism 22, and FIG. 15 is a view of FIG.

As shown in FIG. 13, the clutch mechanism 22 includes an interlocking shaft 27, a clutch piece 28, a coil spring 29, and a solenoid 30. The interlocking shaft 27 is rotatably inserted with respect to the motor shaft 19a, and is configured such that the closer to the motor 19 has a smaller diameter and the farther has a larger diameter. As shown in FIG. 14, the small-diameter portion 27a, which is a small-diameter portion of the interlocking shaft 27, is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °. The large-diameter portion 27b, which is the large-diameter portion of the interlocking shaft 27, has a gear-like periphery, and is connected to a first transmission gear 31 described later so that power can be transmitted. A connecting portion 19b formed integrally with the motor shaft 19a is formed adjacent to the small diameter portion 27a of the interlocking shaft 27 and closer to the motor 19 than the small diameter portion 27a of the interlocking shaft 27. As shown in FIG. 14, the connecting portion 19b is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °, and has the same shape as the small diameter portion 27a of the interlocking shaft 27. . The clutch piece 28 is made of a magnetic material. As shown in FIG. 14, the outer peripheral side is formed in a circular shape, and the inner peripheral side is formed so that a part thereof is depressed in the radial direction every 90 °. The small diameter portion 27a of the interlocking shaft 27 and the outer periphery of the connecting portion 19b are configured to fit on the inner peripheral side. A coil spring 29 is compressed and disposed between the large-diameter portion 27b of the interlocking shaft 27 and the clutch piece 28, and urges the clutch piece 28 to be engaged only with the connecting portion 19b. As shown in FIG. 13, a solenoid 30 that generates a magnetic force and generates a repulsive force on the clutch piece 28 is disposed on the outer peripheral side of the clutch piece 28. The solenoid 30 moves the clutch piece 28 against the urging force of the coil spring 29 by driving, and engages the clutch piece 28 with the connecting portion 19b and the small diameter portion 27a as shown in FIG. The urging force is adjusted so as to transmit the 19 rotational driving force to the transmission mechanism 23.

  As shown in FIG. 13, the transmission mechanism unit 23 includes a first transmission gear 31 and a second transmission gear 32. As shown in FIG. 15, the first transmission gear 31 is provided below the large-diameter portion 27 b of the interlocking shaft 27, and the outer peripheral gear and the gear of the large-diameter portion 27 b of the interlocking shaft 27 are fitted. The rotational driving force of the interlocking shaft 27 is transmitted to the second transmission gear 32 disposed below the interlocking shaft 27. As shown in FIG. 14, the second transmission gear 32 is formed so that one side in the rotation axis direction is a small-diameter portion 32a that is a small-diameter gear, and the other side is a large-diameter portion 32b that is a large-diameter gear. Yes. In the second transmission gear 32, the small diameter portion 32a is engaged with the first transmission gear 31, and the large diameter portion 32b is engaged with a shaft gear 33 described later. Communicate to The clutch mechanism 22 and the transmission mechanism unit 23 are examples of the transmission unit.

In the present embodiment, the heat exchanging unit 24 as a heating and dehumidifying device uses a parallel type two-piston Stirling refrigerator. As shown in FIG. 13, the shaft gear 33, the crankshaft 34, the heat absorption side crank 35a, the heat generation side crank 35b, the heat absorption side piston 36a, the heat generation side piston 36b, the low temperature chamber 37a, the high temperature chamber 37b, the heat absorption head 38a, and the heat generation head 38b. And a regenerator 39. The shaft gear 33 is disposed below the large-diameter portion 32 b of the second transmission gear 32 and is engaged with the gear of the large-diameter portion 32 b of the second transmission gear 32. The shaft gear 33 is integrally attached with a crankshaft 34 that extends toward the front side of the product. The crankshaft 34 is rotatably supported at two places on the installation base 18, and a heat absorption side crank connection portion 34 a and a heat generation side crank connection portion 34 b are provided between the portions that are supported by the shaft. In FIG. 13, the heat absorption side crank connection portion 34a is bent so as to protrude upward, and the heat generation side crank connection portion 34b is bent so as to protrude toward the front side, and the shaft gear 33 is formed as shown in FIG. 1 is rotated counterclockwise (counterclockwise) as viewed from the rear, and the heat generating side crank connecting portion 34b is rotated at a phase advanced by 90 ° with respect to the heat absorbing side crank connecting portion 34a. head 38a of the air passing wind path 25 cooled, heating head 38b is operated to perform the heating of the air passing air path 25.

  The heat absorption side crank connection part 34a and the heat generation side crank connection part 34b are connected to one end of the heat absorption side crank 35a and the heat generation side crank 35b. The heat absorption side crank 35a and the heat generation side crank 35b are connected to the other end of the heat absorption side piston 36a and the heat generation side piston 36b, respectively. Below the heat absorption side piston 36a and the heat generation side piston 36b, there are provided a low temperature chamber 37a and a high temperature chamber 37b in which a gas such as hydrogen or helium is sealed with the installation base 18 as an outline, respectively. The inner surface of the low greenhouse 37a and the heat generating side piston 36b and the inner surface of the high temperature chamber 37b are configured to be airtight and slidable. The tip portions protruding into the ventilation path 25 below the low greenhouse 37a and the high temperature chamber 37b function as a heat absorption head 38a that cools the air in the ventilation path 25 and a heat generation head 38b that heats the air in the ventilation path 25. The heat absorbing head 38a and the heat generating head 38b do not necessarily have to protrude into the ventilation path 25, but are preferably protruded into the ventilation path 25 in order to improve heat exchange efficiency. This cooling and heating function will be described later. Further, the low temperature chamber 37a and the high temperature chamber 37b have paths that allow the rooms to communicate with each other, and a regenerator 39 is disposed in the path. The regenerator 39 has an effect of storing heat from the high-temperature gas passing through the periphery or supplying the stored heat to the low-temperature gas. The heat absorption head 38a and the heat generation head 38b are arranged so that the arrangement directions thereof coincide with the projection axis of the rotation axis of the rotation tank 5 onto the horizontal plane, and vibration that vibrates integrally with the water tank 3 in the main body 1 during operation. The body's center of gravity is pushed down to make it easier to reduce vibration. Thereby, even when the rotating tub 5 is arranged at a high position, the laundry can be easily taken out while contributing to the noise reduction. The installation base 18 is an example of a housing.

  Next, the operation of this washing / drying machine will be described. In the washing / drying machine having the configuration, the user turns on the power, puts the laundry into the rotating tub 5 from the insertion port, and puts the detergent into the detergent case 9, and then presses a start switch on an operation panel (not shown). When the operation is started, the control unit supplies water to the water tank 3 through the water supply port 7, the water supply channel 8, the detergent case 9 and the water supply pipe 10. When the water level sensor 14 detects that the water level in the water tank 3 has reached a predetermined water level, the control unit stops water supply to the water tank 3 and drives the motor 19 to rotate the rotating tank 5 at a low speed. Perform the washing process.

When the washing process is completed, the water in the water tank 3 is discharged out of the machine through the drain pipe 11, the filter device 12, the drain path 15, the drain valve 16 and the drain hose 17, and then the rotating tank 5 is rotated at high speed. To dehydrate the washing water contained in the laundry. When the dehydration process is completed, a rinsing process for rotating the rotating tank 5 at a low speed is started again after water supply to the predetermined level in the water tank 3. When the rinsing step is completed, the dewatering step is performed after the washing water in the water tank 3 is drained. After the rinsing process and the dehydrating process are repeated a plurality of times, the process proceeds to the drying process.

  Next, operation | movement of the principal part of the drying process of Embodiment 2-1 of this invention is demonstrated using FIGS. 16-19. FIG. 16 is an enlarged view of a main part in a state where the clutch mechanism 22 is switched so as to transmit the rotational driving force to the heat exchanging unit 24, and FIG. 17 is a state where the crankshaft 34 is rotated by 90 ° from the state of FIG. FIG. 18 is an enlarged view of a main part, and FIG. 19 is an enlarged view of a main part when the crankshaft 34 is rotated 180 ° from the state of FIG. 16, and FIG. 19 is a state where the crankshaft 34 is rotated 270 ° from the state of FIG. It is a principal part enlarged view.

  When the drying process is started, the blower 26 is driven to blow the air in the ventilation path 25, and the solenoid 30 is driven to engage the clutch piece 28 with the connecting portion 19b and the interlocking shaft 27. This rotational drive force can be transmitted to the interlocking shaft 27. In this state, when the motor 19 is rotated clockwise as shown in FIG. 15, the rotating tub 5 is rotated clockwise as viewed from the rear, and the interlocking shaft 27 is also rotated in the same arrow a direction. The first transmission gear 31 is rotated counterclockwise in the direction of arrow b. The rotational driving force transmitted to the first transmission gear 31 is transmitted to the second rotation gear 32 fitted to the first transmission gear 31 to rotate the second transmission gear 32 in the direction of arrow c. The second transmission gear 32 that rotates in the direction of the arrow c rotates the shaft gear 33 in the direction of the arrow d to drive the heat exchange unit 24.

  In the state of FIG. 16, while the shaft gear 33 is driven in the direction of the arrow d to reach the state of FIG. 17, the heat absorption side crank connection portion 34a and the heat generation side crank connection portion 34b are connected to the heat absorption side crank 35a and the heat generation side crank 35b. Is driven downward, and the gas in the low temperature chamber 37a and the high temperature chamber 37b is compressed by the heat absorption side piston 36a and the heat generation side piston 36b having a phase difference of 90 degrees. At this time, the compressibility of the gas in the high temperature chamber 37b is much larger than that in the low temperature chamber 37a, and the pressure and temperature of the gas in the high temperature chamber 37b increase. Therefore, the temperature of the heating head 38b increases and the high pressure in the high temperature chamber 37b increases. Then, the gas whose temperature has increased is blown into the low temperature chamber 37a through the regenerator 39. When the gas whose temperature has been increased due to the high pressure in the high temperature chamber 37b passes through the regenerator 39, the heat quantity of this gas is stored in the regenerator 39, and the cooled gas is blown into the low temperature chamber 37a. Then, the temperature of the low temperature chamber 37a is lowered.

  While the rotation of the shaft gear 33 progresses and the transition from the state of FIG. 17 to the state of FIG. 18 occurs, the heat absorption side crank connection portion 34a pushes the heat absorption side crank 35a downward. 34b drives the heat generating side crank 35b to lift upward, compresses the gas in the low temperature chamber 37a by the heat absorption side piston 36a, and expands the gas in the high temperature chamber 37b by the heat generation side piston 36b. Moves rapidly through the regenerator 39 to the high temperature chamber 37b. At this time, the gas moving to the high temperature chamber 37b is heated by the amount of heat stored in the regenerator 39, the temperature rises, and the temperature in the high temperature chamber 37b rises.

Further rotates the shaft gear 33, is during the transition to the state of FIG. 19 from the state of FIG. 18, the heat absorption side crank connecting portion 34a and the heating-side crank connecting part 34b is, absorption side crank 35 a Contact and heating The side crank 35b is driven upward and the gas in the low temperature chamber 37a and the high temperature chamber 37b is expanded by the heat absorption side piston 36a and the heat generation side piston 36b. At this time, the expansion coefficient of the gas in the low temperature chamber 37a is much larger than that in the high temperature chamber 37b, and the pressure and temperature of the gas in the low temperature chamber 37a decrease, so the temperature of the heat absorbing head 38a decreases.

  Further, while the shaft gear 33 is rotated to shift from the state shown in FIG. 19 to the state shown in FIG. 16, the heat absorption side crank connection portion 34a moves upward in the direction of lifting the heat absorption side crank 35a. 34b drives the heat generating side crank 35b to push downward, expands the gas in the low temperature chamber 37a by the heat absorbing side piston 36a, and compresses the gas in the high temperature chamber 37b by the heat generating side piston 36b. Moves rapidly through the regenerator 39 to the cold chamber 37a. At this time, the amount of heat of the gas moving to the low temperature chamber 37a is stored in the regenerator 39, and the gas whose temperature has decreased is blown into the low temperature chamber 37a. As the shaft gear 33 rotates in this manner, the heat absorbing head 38a cools and the heat generating head 38b generates heat, and the temperature decreases and increases according to the rotational speed of the shaft gear 33, respectively.

  In the drying process, the air discharged from the water tank 3 into the ventilation path 25 through the exhaust port 25a is sent to the heat absorbing head 38a through the blower 26. The air sent to the heat absorbing head 38a is cooled and dehumidified by the heat absorbing head 38a, and then sent to the heat generating head 38b. The air sent to the heat generating head 38b is heated by the heat generating head 38b and blown into the water tub 3 to evaporate the moisture of the laundry in the rotating tub and advance the drying. Thereafter, the end of drying is detected by detection of a humidity sensor, a temperature sensor or the like (not shown), and the operation is terminated. A drainage hole (not shown) is provided at the bottom of the ventilation path 25 below the heat absorption head 38a. When water (drain water) is condensed on the bottom heat absorption head 38a, the ventilation path 25 and the drainage hose 17 are connected to the drainage hole from the drainage hole. Drained by a connecting drain hose.

As described above, according to the embodiment 2-1 of the present invention, by providing the clutch mechanism 22 on the motor shaft 19a of the motor 19 that rotates the rotating tub 5, the rotational driving force of the motor 19 is applied to the heat exchange unit 24. Since it can transmit and operate the heat exchange part 24, it is not necessary to provide the electric motor which operates a reverse Stirling cycle separately, and a high energy-saving washing machine can be provided. Moreover, since the ventilation path 25 is provided in the lower part in the main body 1, it is not necessary to provide a large space on the top surface of the main body 1 and the upper end of the water tank 3, and the height of the water tank 3 can be increased, so that the laundry can be easily taken out. It can be. Furthermore, since the center of gravity is disposed along the center line below the water tank 3, it can also act as a vibration-preventing weight and can improve the quietness. Further, since a part of the ventilation path 25 is disposed below the heat exchange unit 24 and above the drainage channel 15 or the drainage hose 17, that is, between both, drainage of drain water cooled and dehumidified by the heat exchange unit The route can be shortened and drained quickly.

(Embodiment 2-2)
Hereinafter, Embodiment 2-2 of the present invention will be described with reference to FIGS. 20 is a cross-sectional view of a drum type washer / dryer provided with the heating and dehumidifying device of the present invention according to Embodiment 2-2 of the present invention, FIG. 21 is an enlarged view of the main part of FIG. 20, and FIG. FIG. 23 is an exploded perspective view of the configuration around the motor shaft 40b. In the embodiment 2-2, the same components as those in the embodiment 2-1 are denoted by the same reference numerals and the description thereof is omitted.

In Embodiment 2-2, a drive unit 40 and a ventilation path 41 which are examples of a motor are provided on the back surface of the water tank 3. As shown in FIG. 21, the drive unit 40 has an outer cover covered with a motor cover 40a, and a motor shaft 40b, one end of which is connected to the center of the back surface of the rotating tub 5, is freely rotatable by a bearing 40c. It is supported by. This other end of the motor shaft 40b, and the rotor 40d is attached, Ru Tei has a configuration of a direct-drive system of the inner rotor type that gives rotational driving force by the stator 40e provided on the outer peripheral side thereof. Further, the motor shaft 40b is provided with a connecting portion 40f in which a part of the motor shaft 40b has a large diameter. As shown in FIG. 23, the connecting portion 40f is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °.

  A ventilation path 41 is provided from the back surface of the water tank 3 to the peripheral surface. The ventilation path 41 provided on the back side is arranged so as to surround the outer periphery of the drive unit 40 in the clockwise direction from above so as to substantially follow the peripheral edge of the back surface of the water tank 3. The peripheral surface is provided so as to extend forward. As shown in FIG. 22, the ventilation path 41 is formed between an exhaust port 41a that is a communication port with the inside of the water tank 3, a casing 41b that is an outline of the ventilation path 41, a rear surface of the water tank 3, and the casing 41b. A water tank back surface path 41c, a blower 41d that is an air flow source of the air flow path 41, and a water tank peripheral surface path 41e formed between the water tank 3 peripheral surface and the casing 41b. An absorptive head 54a and a heat generating head 54b of a heat exchanging section 48, which will be described later, protrude from the aquarium back path 41c, and the air in the aquarium back path 41c is cooled and dehumidified and heated by the heat absorbing head 54a and the exothermic head 54b. To be served. Moreover, although not shown in figure, the air supply opening to the water tank 3 of the water tank peripheral surface path | route 41e is distribute | arranged so that the air which passed the ventilation path 41 may be blown in into the rotation tank 5 from the opening part 5a of the rotation tank 5. FIG. Yes. The blower 41d is an example of the fan, and the water tank back surface path 41c and the water tank peripheral surface path 41e are examples of the circulation duct.

As shown in FIG. 21, an interlocking shaft 42 is rotatably disposed on the outer periphery of the motor shaft 40b adjacent to the connecting portion 40f. As shown in FIG. 23, the interlocking shaft 42 is configured such that a portion adjacent to the connecting portion 40f has a small diameter and a portion away from the connecting portion 40f has a large diameter. As shown in FIG. 23, the small-diameter portion 42a, which is a small-diameter portion of the interlocking shaft 42, is formed in a cross-shaped cross section so that a portion projects in the radial direction every 90 °, and is formed in the same shape as the connecting portion 40f. Has been. In contrast, the large-diameter portion 42b, which is the large-diameter portion of the interlocking shaft 42, is formed in a gear shape, and this gear is connected to a transmission gear 46, which will be described later, so as to transmit the rotational driving force. Yes.

As shown in FIG. 21, a clutch piece 43 is provided on the outer periphery of the connecting portion 40f. The clutch piece 43 is made of a magnetic material. As shown in FIG. 23, the outer peripheral side is formed in a circular shape, and the inner peripheral side is formed so as to be partially recessed in the radial direction every 90 °. The small-diameter portion 42a of the interlocking shaft 42 and the outer periphery of the connecting portion 40f are configured to fit on the inner peripheral side. A coil spring 44 is compressively disposed between the large-diameter portion 42b of the interlocking shaft 42 and the clutch piece 43, and urges the clutch piece 43 to be engaged only with the connecting portion 40f. As shown in FIG. 21, a solenoid 45 that generates a magnetic force to generate a repulsive force on the clutch piece 43 is disposed on the outer peripheral side of the clutch piece 43. The solenoid 45 moves the clutch piece 43 against the urging force of the coil spring 44 by driving, and causes the clutch piece 43 to be fitted to both the connecting portion 40f and the interlocking shaft 42 so that the rotational driving force of the motor shaft 40b is described later. The urging force is adjusted so as to be transmitted to the transmission gear 46.

  A transmission gear 46 is disposed below the large-diameter portion 42b of the interlocking shaft 42 as shown in FIG. The transmission gear 46 is connected to the gear of the large-diameter portion 42b of the interlocking shaft 42 above the transmission gear 46, and is also connected to the gear portion of the crank gear 47 provided below the transmission gear 46. The crank gear 47 is perpendicular to the surface of the small diameter gear portion 47a (the broken line portion in FIG. 23), the disk-shaped large diameter portion 47b, and the surface of the large diameter portion 47b opposite to the surface on which the gear portion 47a is provided. It is comprised from the cylindrical crankpin 47c which protrudes. A heat exchanging portion 48 is provided below the crank gear 47 as shown in FIG. The interlocking shaft 42, the clutch piece 43, the coil spring 44, the solenoid 45, the transmission gear 46, and the crank gear 47 are examples of the transmission unit.

  Here, the heat exchange part 48 is demonstrated using FIG. 24 is a cross-sectional view taken along the line CC of FIG.

  As the heat dehumidifying device, the heat exchanging unit 48 uses a V-type two-piston Stirling refrigerator in the present embodiment. As shown in FIG. 24, the outer shell is integrally formed with the motor cover 40a, the heat absorption side crank 49a, the heat generation side crank 49b, the heat absorption side cross head 50a, the heat generation side cross head 50b, the heat absorption side piston pin 51a, the heat generation. Side piston pin 51b, heat absorption side piston 52a, heat generation side piston 52b, low temperature chamber 53a, high temperature chamber 53b, heat absorption head 54a, heat generation head 54b, low temperature chamber air inlet / outlet 55a, high temperature chamber air inlet / outlet 55b, low temperature air passage 56a, high temperature air A passage 56b and a regenerator 57 are provided.

One end of each of the heat absorption side crank 49a and the heat generation side crank 49b is rotatably connected to the crank pin 47c. On the other hand, the other end of the heat-absorbing-side crank 49a and the heating-side crank 49b is pivotally connected to the heat absorbing side crosshead 50a and the heating side crosshead 50b, the rotational driving force of the driving unit 40 that will be transmitted from the crank pin 47c To communicate. The heat absorption side cross head 50a and the heat generation side cross head 50b are fitted in a swingable manner with the inner peripheral surface of the cylindrical motor cover 40a, and are transmitted from the heat absorption side crank 49a and the heat generation side crank 49b. The driving force is transmitted in the axial direction of each piston pin to the heat absorption side piston pin 51a and the heat generation side piston pin 51b connected to the heat absorption side crosshead 50a and the heat generation side crosshead 50b. The heat absorption side piston pin 51a and the heat generation side piston pin 51b are arranged so that the axial directions thereof are substantially perpendicular when viewed from the back side of the water tank 3.

  Further, one end of the heat absorption side piston pin 51a and the heat generation side piston pin 51b is connected to the heat absorption side cross head 50a and the heat generation side cross head 50b, and the other end is connected to the heat absorption side piston 52a and the heat generation side piston 52b. . The heat absorption side piston 52a and the heat generation side piston 52b are slidable with the inner peripheral surface of the motor cover 40a formed in a cylindrical shape, and between the heat absorption side piston 52a and the heat generation side piston 52b and the inner peripheral surface of the motor cover 40a. These sliding surfaces are fitted so as to be hermetically sealed. A low temperature chamber 53a and a high temperature chamber 53b are provided on the side of the heat absorption side piston 52a and the heat generation side piston 52b opposite to the surface on which the heat absorption side piston pin 51a and the heat generation side piston pin 51b are attached. The tip end side is closed by the heat absorbing head 54a and the heat generating head 54b.

The low greenhouse 53a and the high temperature chamber 53b have a low temperature room air inlet / outlet 55a and a high temperature room air inlet / outlet 55b that open toward the rear side of the main body, and the low temperature through the low temperature room air inlet / outlet 55a and the high temperature room air inlet / outlet 55b, respectively. It communicates with the air passage 56a and the hot air communication passage 56b. The path between the cold air passage 56a and the hot air through passage 56b, the regenerator 57 is connected. Air cold chamber 53a is cold room air inlet and outlet 55a by the operation of the heat absorption side piston 52a, the low-temperature air passage 56a, fed regenerator 57, hot air communication passage 56b, through the hot chamber air inlet and outlet 55b into the hot chamber 53b on the contrary, the air in the hot chamber 53b, the hot compartment air inlet and outlet 55b by the operation of the heating side piston 52 b, hot air passage 56b, the regenerator 57, cold air communication passage 56a, the cold room via a cold room air entrance 55a 53a. In this case, regenerator 57 absorbs heat of the air flowing from the hot air through passage 56b, and discharges the heat to the air flowing from the cold air communication passage 56a, the air in the cold chamber 53a is low, the high temperature chamber 53b The air acts to maintain a high temperature.

  Next, operation | movement of the principal part of the drying process of Embodiment 2-2 of this invention is demonstrated using FIG. 22, FIG. 24-FIG. FIG. 25 is an enlarged view of a main part when the crank gear 47 is rotated 90 ° from the state of FIG. 24, and FIG. 26 is an enlarged view of a main part of the state where the crank gear 47 is rotated 180 ° from the state of FIG. FIG. 27 is an enlarged view of a main part in a state where the crank gear 47 is rotated by 270 ° from the state of FIG.

  When the drying process is started, the blower 41d is driven to blow air in the ventilation path 41, and the solenoid 45 is driven to engage the clutch piece 43 with the connecting portion 40f and the interlocking shaft 42, thereby driving the driving portion. Forty rotational driving forces can be transmitted to the interlocking shaft 42. In this state, when the drive unit 40 is rotated in the direction of the arrow e, which is clockwise as shown in FIG. 22, the rotating tub 5 is rotated clockwise around the motor shaft 40b when viewed from the rear, and interlocked. The shaft 42 is also rotated in the same arrow e direction, and the transmission gear 46 is rotated in the counterclockwise arrow f direction. The rotational driving force transmitted to the transmission gear 46 rotates the crank gear 47 fitted thereto in the direction of the arrow g to drive the heat exchanging unit 48.

In the state of FIG. 24, while the crank gear 47 is in a state of FIG. 25 is driven in the arrow g Direction in FIG 22, the heat absorption side crank 49a is in the direction of lifting the absorption side crosshead 50a upward, heating side The crank 49b drives the heat generation side crosshead 50b in a direction to push it downward, expands the gas in the low temperature chamber 53a by the heat absorption side piston 52a, and compresses the gas in the high temperature chamber 53b by the heat generation side piston 52b. The gas in the chamber 53b moves rapidly through the regenerator 57 to the low temperature chamber 53a. At this time, the amount of heat of the gas moving to the low temperature chamber 53a is stored in the regenerator 57, and the gas whose temperature has decreased is blown into the low temperature chamber 53a .

  While the rotation of the crank gear 47 advances and the state of FIG. 25 shifts to the state of FIG. 26, the heat absorption side crank 49a and the heat generation side crank 49b are connected to the heat absorption side cross head 50a and the heat generation side cross head 50b. Driven upward, the gas in the low temperature chamber 53a and the high temperature chamber 53b is expanded by the heat absorption side piston 52a and the heat generation side piston 52b. At this time, the expansion coefficient of the gas in the low temperature chamber 53a is much larger than that in the high temperature chamber 53b, and the pressure and temperature of the gas in the low temperature chamber 53a decrease, so the temperature of the heat absorbing head 54a decreases.

While the rotation of the crank gear 47 advances and the state of FIG. 26 shifts to the state of FIG. 27, the heat absorption side crank 49a pushes the heat absorption side crosshead 50a downward, and the heat generation side crank 49b generates heat. The side crosshead 50b is driven upward, the gas in the low temperature chamber 53a is compressed by the heat absorption side piston 52a, and the gas in the high temperature chamber 53b is expanded by the heat generation side piston 52b, so that the gas in the low temperature chamber 53a is regenerated. It moves rapidly through the vessel 57 to the high temperature chamber 53b. At this time, the gas moving to the high temperature chamber 53b is heated by the amount of heat stored in the regenerator 57, the temperature rises, and the temperature in the high temperature chamber 53b rises.

  While the rotation of the crank gear 47 advances and the transition from the state of FIG. 27 to the state of FIG. 24 is performed, the heat absorption side crank 49a and the heat generation side crank 49b move the heat absorption side cross head 50a and the heat generation side cross head 50b. The gas is driven in a downward direction and compressed in the low temperature chamber 53a and the high temperature chamber 53b by the heat absorption side piston 52a and the heat generation side piston 52b. At this time, the compressibility of the gas in the high temperature chamber 53b is much larger than that in the low temperature chamber 53a, and the pressure and temperature of the gas in the high temperature chamber 53b increase. Therefore, the temperature of the heat generating head 54b increases and the high pressure in the high temperature chamber 53b increases. Then, the gas whose temperature has increased is blown into the low temperature chamber 53a through the regenerator 57. When the gas whose temperature has been increased due to the high pressure in the high temperature chamber 53b passes through the regenerator 57, the heat quantity of this gas is stored in the regenerator 57, and the cooled gas is blown into the low temperature chamber 53a by depriving the heat quantity. Then, the temperature of the low temperature chamber 53a is lowered. As the crank gear 47 rotates in this manner, the heat absorbing head 54a cools and the heat generating head 54b generates heat, and the temperature decreases and rises according to the rotational speed of the crank gear 47, respectively.

In the drying step, the air discharged into the ventilation path 41 from the water tank 3 through the exhaust port 41a passes through the fan 41 d, is sent to the heat absorbing head 54a. The air sent to the heat absorbing head 54a is cooled and dehumidified by the heat absorbing head 54a, and then sent to the heat generating head 54b. The air sent to the heat generating head 54b is heated by the heat generating head 54b and blown into the water tub 3 through the air supply port described above to evaporate the moisture of the laundry in the rotating tub and proceed with drying. Let Thereafter, the end of drying is detected by detection of a humidity sensor, a temperature sensor or the like (not shown), and the operation is terminated. The water tank back path 41 c bottom of the lower heat absorption head 54a, and a drain hole (not shown) is provided, the water condensed on the heat absorption head 54a (the drain water) is added dropwise, from the drain hole and the water tank back path 41 c drainage The water is drained by a drain hose connecting the hose 17.

  As mentioned above, according to Embodiment 2-2 of this invention, in addition to the effect by Embodiment 2-2 mentioned above, the empty space below the direct drive type drive part 40 provided in the water tank 3 back surface In addition, since the heat exchanging portion 48 can be arranged through the clutch mechanism so that the reverse Stirling cycle has a substantially inverted V shape or C shape, a space-saving washing machine can be provided.

In addition, in order to facilitate the removal of the laundry, when applied to the construction of a drum-type washing machine in which the openings of the water tub 3 and the rotating tub 5 are arranged obliquely upward, the water tank 3 and the lower part of the main body 1 The space can be used effectively, and the center of gravity is lowered because the heat exchanging unit 48 is disposed below the driving unit 40. In addition, the heat absorption head 54a side and the heat generation head 54b side of the heat exchange unit 48 are arranged in a substantially reverse V-order shape across a vertical center line passing through the motor shaft 58b of the drive unit 40 which is a heavy object, so that vibrations It can also act as a weight for prevention, and can improve the quietness.

(Embodiment 2-3)
Embodiment 2-3 of the present invention will be described below with reference to FIGS. 28 is a cross-sectional view of a drum type washer / dryer provided with the heating and dehumidifying device of the present invention according to Embodiment 2-3 of the present invention, FIG. 29 is an enlarged view of the main part of FIG. 28, and FIG. FIG. 31 is an exploded perspective view of the configuration around the motor shaft 58b. In this embodiment 2-3, the same components as the implementation form 2-2 will be omitted with denoted by the same reference numerals.

  In Embodiment 2-3, the drive part 58 which is an example of a motor is provided in the back surface of the water tank 3. FIG. As shown in FIG. 29, the drive unit 58 is covered with a motor cover 58a, and a motor shaft 58b, one end of which is connected to the center of the back surface of the rotary tub 5, is freely rotatable by a bearing 58c. It is supported by. A rotor 58e is attached to the other end of the motor shaft 58b, and has a configuration of an outer rotor type direct drive system in which a rotational driving force is applied by a stator 58d provided on the outer peripheral side thereof. Yes. Further, the motor shaft 58b is provided with a connecting portion 58f in which a part of the motor shaft 58b has a large diameter. As shown in FIG. 31, the connecting portion 58f is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °.

On the outer periphery of the motor shaft 58b, as shown in FIG. 29, an interlocking shaft 59 is rotatably disposed adjacent to the connecting portion 58f. The interlocking shaft 59 is configured such that a portion adjacent to the connecting portion 58f has a small diameter, and a separated portion has a large diameter. As shown in FIG. 31, the small-diameter portion 59a, which is the small-diameter portion of the interlocking shaft 59, is formed in a cross-shaped cross section so that a portion protrudes in the radial direction every 90 °, and is formed in the same shape as the connecting portion 58f. Has been. On the other hand, the large-diameter portion 59b, which is the large-diameter portion of the interlocking shaft 59, is formed in a gear shape, and this gear is connected to a connecting gear 63, which will be described later, so as to transmit a rotational driving force. Yes.

A clutch piece 60 is provided on the outer periphery of the connecting portion 58f as shown in FIG. The clutch piece 60 is made of a magnetic material. As shown in FIG. 31, the outer peripheral side is formed in a circular shape, and the inner peripheral side is formed so that a part thereof is depressed in the radial direction every 90 °. The small diameter portion 59a of the interlocking shaft 59 and the outer periphery of the connecting portion 58f are configured to fit on the inner peripheral side. A coil spring 61 is compressed between the large-diameter portion 59b of the interlocking shaft 59 and the clutch piece 60, and urges the clutch piece 60 to be engaged only with the connecting portion 58f. On the outer peripheral side of the clutch piece 60, as shown in FIG. 29, a solenoid 62 that generates a magnetic force to generate a repulsive force on the clutch piece 60 is disposed. The solenoid 62 moves the clutch piece 60 against the urging force of the coil spring 61 by the drive, and engages the clutch piece 60 with both the connecting portion 58f and the interlocking shaft 59, so that the rotational driving force of the motor shaft 58b is described later. To the connecting gear 63 to be transmitted.

A connecting gear 63 is disposed below the large-diameter portion 59b of the interlocking shaft 59 as shown in FIG. The connecting gear 63 is connected to the gear of the large-diameter portion 59b of the interlocking shaft 59 above the connecting gear 63, and is also connected to the slide gear 64 arranged in the gear shaft direction. The slide gear 64 is coupled to the first small transmission gear 65 or the transmission gear 67 below the slide gear 64, and the first small transmission gear 65 is coupled to the second small transmission gear 66 below the slide gear 64. Further, the second small transmission gear 66 and the transmission gear 67 are connected to the crank gear 68 below the second small transmission gear 66 and the transmission gear 67. The crank gear 68 projects vertically from a surface opposite to the surface on which the small-diameter gear portion 68a (the broken line portion in FIG. 31), the disk-shaped large-diameter portion 68b, and the large-diameter gear portion are provided. It is comprised from the cylindrical crankpin 68c which carries out. A heat exchanging section 48 is provided below the crank gear 68, as shown in FIG. In the present embodiment, the heat exchanging unit 48 uses a V-type two-piston Stirling refrigerator as in the case of the embodiment 2-2 . The interlocking shaft 59, the clutch piece 60, the coil spring 61, the solenoid 62, the coupling gear 63, the slide gear 64, the first small transmission gear 65, the second small transmission gear 66, the transmission gear 67, and the crank gear 68 are transmitted. It is an example of a part.

  Here, the connection gear 63 and the slide gear 64 will be described with reference to FIG. 32A is a top view of the slide gear 64, FIG. 32B is a view as viewed from the arrow F in FIG. 32A, FIG. 32C is a view as viewed from the arrow G in FIG. , (E) is a view taken in the direction of arrow H in (d), (f) is a sectional view taken along the line II in (e), (g) is a sectional view taken along the line JJ in (e), and (h) is a sectional view in (e). KK sectional drawing, (i) is LL sectional drawing of (e).

  As shown in FIGS. 32A to 32C, the slide gear 64 includes a gear portion 64b, a cylindrical portion 64a extending in the gear shaft direction from one side surface of the gear portion 64b, and a tip of the cylindrical portion 64a. A cylindrical pin portion 64c extending in a direction perpendicular to the cylinder axis and a cylindrical pin portion 64d extending in a direction opposite to the pin portion 64c are configured. As shown in FIGS. 32D to 32I, the connecting gear 63 includes a gear portion 63b, a cylindrical portion 63a extending in the gear axis direction from one side surface of the gear portion 63b, and a cylindrical axis direction of the cylindrical portion 63a. And a hole 63c into which the cylindrical part 64a is inserted, and a pin part 64d of the slide gear 64 is inserted in a spiral shape perpendicularly to the peripheral surface of the hole 63c and the pin part 64d is cylindrical. A slide hole 63d formed so as to be slidable approximately 180 degrees around the cylindrical axis of the portion 64a, and a pin portion 64c of the slide gear 64 inserted into the spiral shape perpendicularly to the peripheral surface of the hole 63c and the pin The portion 64c includes a slide hole 63e formed so as to be slidable approximately 180 degrees around the cylinder axis of the cylinder portion 64a.

  Next, the operation when the connecting gear 63 is given a rotational driving force from the interlocking shaft 59 will be described. First, when the connecting gear 63 is connected to the first small transmission gear 65, the connecting gear 63 receives a rotational driving force from the interlocking shaft 59, and the clockwise (clockwise) direction in FIG. , The pin portion 64c slides the slide hole 63e, the pin portion 64d slides the slide hole 63d about 180 degrees around the column axis of the column portion 64a, and the column portion 64a slides in a direction to come out of the hole portion 63c. . That is, the gear portion 64 b slides toward the front side in FIG. 31 to release the connection with the first small transmission gear 65 and to connect with the transmission gear 67. On the contrary, when the connecting gear 63 is connected to the transmission gear 67, the connecting gear 63 receives a rotational driving force from the interlocking shaft 59, and rotates in the counterclockwise (counterclockwise) direction in FIG. When moved, the pin portion 64c slides the slide hole 63e, the pin portion 64d slides the slide hole 63d approximately 180 degrees around the cylinder axis of the cylinder portion 64a, and the cylinder portion 64a slides in a direction to enter the hole portion 63c. That is, the gear portion 64b slides to the back side in FIG. 31 to release the connection with the transmission gear 67 and to connect with the first small transmission gear 65. In this way, regardless of whether the rotation direction of the drive unit 58 is forward or reverse, the connection with the slide gear 64 is switched to the first small transmission gear 65 or the transmission gear 67 to thereby change the crank gear 68. The rotation direction can be a constant direction.

  Next, operation | movement of the principal part of the drying process of Embodiment 2-3 of this invention is demonstrated using FIGS. 33-36. 33 is a cross-sectional view taken along the line E-E in FIG. 29, FIG. 34 is an enlarged view of a main part of the state where the crank gear 68 is rotated by 90 ° from the state of FIG. 33, and FIG. 36 is an enlarged view of a main part in a state in which the crank gear 68 is rotated by 270 ° from the state of FIG. 33. FIG.

  When the drying process is started, the blower 41d is driven to blow air in the ventilation path 41, and the solenoid 62 is driven to engage the clutch piece 60 with the connecting portion 58f and the interlocking shaft 59, thereby driving the driving portion. The rotational driving force 58 can be transmitted to the interlocking shaft 59. In this state, the rotational driving force of the drive unit 58 is changed from the interlocking shaft 59 to the coupling gear 63 to the slide gear 64 to the transmission gear 67 (or the first small transmission gear 65 to the second small transmission gear 66) to the crank gear 68. Communicated. Thereby, the crank gear 68 rotates in the counterclockwise (counterclockwise) direction in FIG. 33 and the heat exchanging unit 48 is driven.

In the state shown in FIG. 33, while the crank gear 68 is driven in the counterclockwise (counterclockwise) direction to reach the state shown in FIG. 34, the heat absorption side crank 49a generates heat in the direction of lifting the heat absorption side crosshead 50a upward. The side crank 49b is driven to push the heat generating side crosshead 50b downward, expands the gas in the low temperature chamber 53a by the heat absorption side piston 52a, and compresses the gas in the high temperature chamber 53b by the heat generation side piston 52b. The gas in the high greenhouse 53b passes through the regenerator 57 and rapidly moves to the low temperature chamber 53a. At this time, the amount of heat of the gas moving to the low temperature chamber 53a is stored in the regenerator 57, and the gas whose temperature has decreased is blown into the low temperature chamber 53a .

  While the rotation of the crank gear 68 advances and the state shown in FIG. 34 shifts to the state shown in FIG. 35, the heat absorption side crank 49a and the heat generation side crank 49b move the heat absorption side cross head 50a and the heat generation side cross head 50b. Driven upward, the gas in the low temperature chamber 53a and the high temperature chamber 53b is expanded by the heat absorption side piston 52a and the heat generation side piston 52b. At this time, the expansion coefficient of the gas in the low temperature chamber 53a is much larger than that in the high temperature chamber 53b, and the pressure and temperature of the gas in the low temperature chamber 53a decrease, so the temperature of the heat absorbing head 54a decreases.

While the rotation of the crank gear 68 proceeds and the transition from the state of FIG. 35 to the state of FIG. 36 is performed, the heat absorption side crank 49a pushes the heat absorption side crosshead 50a downward, and the heat generation side crank 49b generates heat. The side crosshead 50b is driven upward, the gas in the low temperature chamber 53a is compressed by the heat absorption side piston 52a, and the gas in the high temperature chamber 53b is expanded by the heat generation side piston 52b, so that the gas in the low temperature chamber 53a is regenerated. It moves rapidly through the vessel 57 to the high temperature chamber 53b. At this time, the gas moving to the high temperature chamber 53b is heated by the amount of heat stored in the regenerator 57, the temperature rises, and the temperature in the high temperature chamber 53b rises.

  While the rotation of the crank gear 68 advances and the state of FIG. 36 shifts to the state of FIG. 33, the heat absorption side crank 49a and the heat generation side crank 49b move the heat absorption side cross head 50a and the heat generation side cross head 50b. The gas is driven in a downward direction and compressed in the low temperature chamber 53a and the high temperature chamber 53b by the heat absorption side piston 52a and the heat generation side piston 52b. At this time, the compressibility of the gas in the high temperature chamber 53b is much larger than that in the low temperature chamber 53a, and the pressure and temperature of the gas in the high temperature chamber 53b increase. Therefore, the temperature of the heat generating head 54b increases and the high pressure in the high temperature chamber 53b increases. Then, the gas whose temperature has increased is blown into the low temperature chamber 53a through the regenerator 57. When the gas whose temperature has been increased due to the high pressure in the high temperature chamber 53b passes through the regenerator 57, the heat quantity of this gas is stored in the regenerator 57, and the cooled gas is blown into the low temperature chamber 53a by depriving the heat quantity. Then, the temperature of the low temperature chamber 53a is lowered. As the crank gear 68 rotates in this manner, the heat absorbing head 54a cools and the heat generating head 54b generates heat, and the temperature decreases and rises according to the rotational speed of the crank gear 68, respectively.

In the drying step, the air discharged into the ventilation path 41 from the water tank 3 through the exhaust port 41a passes through the fan 41 d, is sent to the heat absorbing head 54a. The air sent to the heat absorbing head 54a is cooled and dehumidified by the heat absorbing head 54a, and then sent to the heat generating head 54b. The air sent to the heat generating head 54b is heated by the heat generating head 54b and blown into the water tub 3 to evaporate the moisture of the laundry in the rotating tub and advance the drying. Thereafter, the end of drying is detected by detection of a humidity sensor, a temperature sensor or the like (not shown), and the operation is terminated. The water tank back path 41 c bottom of the lower heat absorption head 54a, and a drain hole (not shown) is provided, the water condensed on the heat absorption head 54a (the drain water) is added dropwise, from the drain hole and the water tank back path 41 c drainage The water is drained by a drain hose connecting the hose 17.

  As mentioned above, according to Embodiment 2-3 of this invention, in addition to the effect by Embodiment 2-1 and 2-2 mentioned above, even if the drive part 58 is rotated forward / reversely, the heat exchange part 48 is carried out. The rotation direction of the crank gear 68 for driving the motor can be set to a constant direction. Thereby, for example, in the drying process, even if the rotating tub 5 is rotated forward and backward in order to release the entanglement of clothes, the heat exchange unit 48 can continue the reverse Stirling cycle, so that uneven drying of clothes, etc. is reduced, Drying time can be shortened.

  In addition, according to Embodiments 2-1 to 2-3 of the present invention, for example, the conventional technique uses an electric heater for heating the circulating air to dry the laundry and uses tap water for cooling and dehumidifying the circulating air. In comparison, the electric power used is only the driving electric power of the motor, and the power consumption can be further reduced. In addition, the amount of tap water used can be reduced.

  In addition, according to Embodiments 2-1 to 2-3 of the present invention, for example, compared with the conventional technique using a heat pump for drying and cooling of the circulating air for drying the laundry, it is used. The power to be used is only the driving power of the motor, and the power consumption can be further reduced.

  According to Embodiments 2-1 to 2-3 of the present invention, the laundry can be dried or the laundry can be washed, dehydrated, and dried with the driving power of the motor that rotates the rotating tub. Compared to a washing and drying machine, it is possible to achieve further reduction in water saving and power consumption.

  In particular, when a Stirling refrigerator is used as the heat exchanger, a reverse Stirling cycle is performed by an interlocking means that transmits the rotational force of the motor to the Stirling refrigerator, and the low temperature chamber and the high temperature chamber of the Stirling refrigerator are used. The drying of the laundry can be realized by heating the circulating air to dry the laundry and cooling and dehumidifying the hot and humid circulating air containing moisture evaporated from the laundry.

  Therefore, it is possible to provide a dryer or a washing dryer that can further reduce power consumption without using water.

  In addition, the structure and control mentioned above may be applied not only to a washing and drying machine but also to a drying machine, and the rotary tank is not limited to a horizontal installation type, may be a vertical installation type, and is not limited to a drum type. .

  In addition, it is as follows when the technical idea of the dryer based on Embodiment 2-1 to 2-3 of this invention is summarized.

  (1) A dryer according to the present invention provides a water tank, a rotary tank rotatably provided in the water tank, a motor for rotating the rotary tank, a circulation duct communicating with the inside of the water tank, and a gas in the water tank. A fan that circulates through the circulation duct, a heat exchange part that performs heat exchange so that the air in the circulation duct is cooled by the heat absorption head and is heated by the heat generation head, and the rotational force of the motor is used to operate the heat exchange part. And a transmission unit that transmits the power for power.

  (2) The dryer according to the present invention is characterized in that the heat exchange section is provided in a water tank.

  (3) In the dryer according to the present invention, the heat exchange part is provided below the water tank.

  (4) In the dryer according to the present invention, the heat exchange part is provided on the back surface of the water tank.

  (5) The dryer according to the present invention is characterized in that the heat exchange section is provided below the motor.

  (6) The dryer according to the present invention is characterized in that at least a part of the circulation duct is disposed below the water tank.

  (7) The dryer according to the present invention is characterized in that at least a part of the circulation duct is disposed on the back surface of the water tank.

  (8) In the dryer according to the present invention, at least a part of the circulation duct is arranged along the peripheral edge of the back surface of the water tank.

  (9) The dryer according to the present invention is characterized in that a part of the circulation duct is arranged between the heat exchange part and a part of the drainage path for draining the liquid in the water tank.

  (10) The dryer according to the present invention is characterized in that the heat absorbing head and the heat generating head protrude into the circulation duct.

  (11) In the dryer according to the present invention, the heat exchange unit is a Stirling refrigerator.

  (12) In the dryer according to the present invention, the Stirling refrigerator includes a semi-hermetic housing, a crankshaft disposed in the housing, a heat absorption side crank and a heat generation side crank connected to the crankshaft, A heat absorption side piston and a heat generation side piston connected to each crank, a working gas is sealed inside, and a low temperature chamber and a high temperature chamber in which each piston reciprocates in conjunction with rotation of the crankshaft. It rotates by a part, It is characterized by the above-mentioned.

  (13) The dryer according to the present invention is characterized in that the heat absorbing head and the heat generating head are part of a low temperature chamber and a high temperature chamber that appear and disappear in the circulation duct.

  (14) In the dryer according to the present invention, the transmission unit includes an interlocking shaft that is engaged with the rotating shaft of the motor via a clutch, and a gear that is connected to the interlocking shaft and rotates the crankshaft. Features.

  (15) In the dryer according to the present invention, the transmission unit rotates the crankshaft in one direction even when the motor rotates forward or backward.

  (16) In the dryer according to the present invention, the transmission unit transmits the rotational force of the motor to the crankshaft, and operates the Stirling refrigerator in a reverse Stirling cycle.

  (17) In the dryer according to the present invention, each piston reciprocates with a phase difference of 90 degrees.

  (18) In the dryer according to the present invention, the clutch is arranged between the first fitting portion provided on the rotating shaft of the motor and the second fitting portion provided on the interlocking shaft. The urging means for urging the clutch toward the first fitting portion is disposed between the clutch and the interlocking shaft.

  (19) The dryer according to the present invention is provided with an electromagnetic coil that generates a magnetic field around the clutch, and energizes the electromagnetic coil so that the clutch is both in the first fitting portion and the second fitting portion. It moves to the position fitted in.

  (20) In the dryer according to the present invention, the gear meshes with the first transmission gear meshed with the interlocking shaft, the first transmission gear and the crank gear provided on the crankshaft, and the rotation shaft of the motor And a second transmission gear that rotates in the opposite direction.

  (21) In the dryer according to the present invention, the crankshaft includes a crankshaft in which connecting portions connected to each crank are provided with a phase difference of 90 degrees, and a crank gear provided on one of the crankshafts The second transmission gear is configured by overlapping a small-diameter gear and a large-diameter gear, and is arranged so that the first transmission gear and the small-diameter gear mesh with each other, and the crank gear and the large-diameter gear mesh with each other. It is characterized by.

  (22) In the dryer according to the present invention, the crankshaft is characterized in that a pin connected to each crank is provided on one side and a crank gear engaged with the gear is provided on the other side.

  (23) In the dryer according to the present invention, the first transmission gear is composed of an interlocking gear that is always connected to the interlocking shaft, and a slide gear that is provided with the same rotational center and position of the interlocking gear, The slide gear is provided so that the distance from the interlocking gear can be changed according to the rotation direction of the interlocking gear, the second transmission gear is always meshed with the crank gear, and the odd-numbered transmission gears having different rotational positions, When the interlocking gear rotates in one direction, the slide gear is connected to the transmission gear, and when the interlocking gear rotates in the other direction, the slide gear is small. It is connected to a transmission gear.

  (24) The dryer according to the present invention is characterized in that the low temperature chamber and the high temperature chamber are arranged in a C shape or an inverted V shape when viewed from the center of the rotating shaft of the motor.

  (25) A laundry dryer according to the present invention is any one of the above-described dryers, wherein the laundry is stored in a rotating tub, and any one of washing, dehydration, and drying is performed. .

  (26) In the washing / drying machine according to the present invention, the rotation axis of the rotating tub is substantially perpendicular to the installation surface.

  (27) In the washing / drying machine according to the present invention, the rotating shaft of the rotating tub is substantially horizontal or oblique with respect to the installation surface.

  The high controllability obtained by using an example of a Stirling engine used in the heating and dehumidifying apparatus as one embodiment of the present invention will be described.

  The characteristics of the Stirling engine and heat pump were confirmed by driving the Stirling engine and heat pump under atmospheric pressure and opening the high temperature side and low temperature side to the atmosphere. The temperature on the high temperature side of the Stirling engine was measured on the heat generating head, and the temperature on the low temperature side was measured on the heat absorbing head. The temperature on the high temperature side of the heat pump was measured in a condenser, and the temperature on the low temperature side was measured in an evaporator. The measured temperature was recorded every 10 seconds. The room temperature was about 27 ° C. The specification of the Stirling engine used as an example is an output of about 250 W, and the refrigerant is helium. Further, the specification of the heat pump used as an example is an output of about 370 W, and the refrigerant is HCF · R134a.

  FIG. 37 is a diagram showing a temporal change in temperature on the high temperature side measured immediately after the start of driving of the Stirling engine and the heat pump.

  As shown in FIG. 37, in the high temperature part of the Stirling engine, the temperature has risen immediately after the start of driving of the Stirling engine. On the other hand, the temperature of the high temperature portion of the heat pump hardly changes immediately after the start of driving of the heat pump, and starts to rise gradually after about 10 seconds.

  FIG. 38 is a diagram illustrating a temporal change in temperature on the high temperature side from the start of driving of the Stirling engine and the heat pump until reaching a predetermined temperature. The predetermined temperature was 60 ° C.

  As shown in FIG. 38, the high temperature side of the Stirling engine reached 60 ° C. in 50 seconds from the start of driving. On the other hand, the high temperature side of the heat pump reached 60 ° C. in 230 seconds from the start of driving. Thus, since the high temperature side of the Stirling engine reaches a predetermined temperature faster than the high temperature side of the heat pump, the high temperature gas is brought into contact with the laundry in the initial stage of the drying process by using the Stirling engine in the dryer. The drying time can be shortened.

  FIG. 39 is a diagram illustrating a temporal change in temperature that changes in 10 seconds with respect to the temperature on the high temperature side measured immediately after the start of driving of the Stirling engine and the heat pump.

  As shown in FIG. 39, it was found that the Stirling engine has a large temperature change amount immediately after the start of driving and has a good responsiveness. On the other hand, the temperature change of the heat pump was hardly measured immediately after the start of driving. This is because it takes a certain amount of time for the refrigerant of the heat pump to change state between the gas and liquid phases, whereas the Stirling engine does not need to change the state of the working gas, so such high responsiveness was obtained. Conceivable.

  FIG. 40 is a diagram showing temporal changes in temperature of the high temperature side and low temperature side of the Stirling engine and the high temperature side and low temperature side of the heat pump measured at intervals of 10 seconds from the start of driving of the Stirling engine and the heat pump until 2 minutes have passed. It is.

  As shown in FIG. 40, immediately after the start of driving of the Stirling engine, the temperature on the high temperature side of the Stirling engine rises quickly, the temperature on the low temperature side of the Stirling engine falls quickly, and after 50 seconds from the start of driving, The high temperature side reached 60 ° C and the low temperature side reached -20 ° C. After that, the speed of temperature change hardly decreased, and after 2 minutes from the start of driving, the high temperature side reached 80 ° C. and the low temperature side reached −60 ° C. On the other hand, the heat pump has almost no temperature change on the high temperature side and the low temperature side immediately after the start of driving, and reaches about 35 ° C. on the high temperature side and about 10 ° C. on the low temperature side from about 10 seconds to 30 seconds after the start of driving. After that, however, the amount of temperature change decreased and showed a moderate temperature change. The temperature on the high temperature side gradually increased until reaching about 48 ° C. from the start of driving for 2 minutes, but reached about 48 ° C., but the temperature on the low temperature side hardly decreased from about 8 ° C.

  Thus, the responsiveness of the Stirling engine is higher than that of the heat pump. Further, the Stirling engine has a wider controllable temperature range than the heat pump. For example, the time required from the start of driving the Stirling engine to 60 ° C on the high temperature side is less than a quarter of the time required from the start of driving the heat pump to 60 ° C on the high temperature side. there were. Therefore, by using a Stirling engine, a dryer having higher controllability than a heat pump can be obtained. As described above, the heating and dehumidifying device including the Stirling engine can shorten the time required to start the heating and dehumidifying device, and is required when the operation is once interrupted and then restarted during the operation of the heating and dehumidifying device. Time can be shortened.

  It should be considered that the embodiments and examples disclosed above are illustrative and non-restrictive in every respect. The scope of the present invention is shown not by the above embodiments and examples but by the scope of claims, and includes all modifications and variations within the meaning and scope equivalent to the scope of claims.

BRIEF DESCRIPTION OF THE DRAWINGS As Embodiment 1-1 of this invention, it is a perspective view which shows roughly the external appearance of the whole washing-drying machine provided with the heating dehumidification apparatus of this invention. It is a sectional side view which shows roughly the cross section which looked at the washing-drying machine of FIG. 1 from the direction of the II-II line. It is sectional drawing which shows the cross section of the whole Stirling engine. It is a perspective view which shows the whole main body of a heating dehumidification apparatus. It is sectional drawing which shows the outline when a washing-drying machine is seen from the direction of the VV line of FIG. As Embodiment 1-2 of this invention, it is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing-drying machine is provided. As Embodiment 1-3 of this invention, it is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing-drying machine is provided. As Embodiment 1-4 of this invention, it is a perspective view which shows another form of the main body of the heating dehumidification apparatus with which a washing-drying machine is provided. As Embodiment 1-5 of this invention, it is a sectional side view which shows roughly the side cross section of a washing-drying machine provided with the heating dehumidification apparatus of this invention. It is sectional drawing which shows roughly the cross section which looked at the washing-drying machine from the back surface. It is sectional drawing which shows the structure of the water supply / drainage system of the drum type washing-drying machine provided with the heating dehumidification apparatus of this invention which concerns on Embodiment 2-1 of this invention. It is sectional drawing which shows the structure of the drying processing system of the drum type washing-drying machine provided with the heating dehumidification apparatus of this invention concerning Embodiment 2-1 of this invention. It is a principal part enlarged view of FIG. It is a schematic diagram of the connection release state of a clutch mechanism. It is a schematic diagram of the connection state of the clutch mechanism and power transmission mechanism seen from A of FIG. It is a principal part enlarged view which shows the 0 degree rotation state of a crankshaft. It is a principal part enlarged view which shows the 90 degree rotation state of a crankshaft. It is a principal part enlarged view which shows the 180 degree rotation state of a crankshaft. It is a principal part enlarged view which shows the 270 degree rotation state of a crankshaft. It is a longitudinal cross-sectional view of the washing-drying machine provided with the heating dehumidification apparatus of this invention which concerns on Embodiment 2-2 of this invention. It is a principal part enlarged view of FIG. It is BB sectional drawing of FIG. It is a schematic diagram of the connection release state of a clutch mechanism. It is CC sectional drawing of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 90 degrees from the state of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 180 degrees from the state of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 270 degrees from the state of FIG. It is a longitudinal cross-sectional view of the washing-drying machine provided with the heating dehumidification apparatus of this invention which concerns on Embodiment 2-3 of this invention. It is a principal part enlarged view of FIG. It is DD sectional drawing of FIG. It is a schematic diagram of the connection release state of a clutch mechanism. It is principal part sectional drawing of a connection gearwheel and a slide gear, (a) is a top view of a slide gear, (b) is F arrow figure of (a), (c) is G arrow figure of (a), ( d) is a top view of the transmission gear, (e) is a view taken in the direction of arrow H in (d), (f) is a sectional view taken along line II in (e), (g) is a sectional view taken along line JJ in (e), (H) is KK sectional drawing of (e), (i) is LL sectional drawing of (e). It is EE sectional drawing of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 90 degrees from the state of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 180 degrees from the state of FIG. It is a principal part enlarged view which shows the state which the crankshaft rotated 270 degrees from the state of FIG. It is a figure which shows the time change of the temperature of the high temperature side measured immediately after the start of a drive of a Stirling engine and a heat pump. It is a figure which shows the time change of the temperature of a high temperature side from the start of a drive of a Stirling engine and a heat pump until it reaches predetermined temperature. It is a figure which shows the time change of the temperature which changes for 10 second about the temperature of the high temperature side measured immediately after the start of a drive of a Stirling engine and a heat pump. It is a figure which shows the time change of the temperature of the high temperature side and low temperature side of a Stirling engine, and the temperature of the high temperature side and low temperature side of a heat pump which were measured at intervals of 10 seconds from the start of driving of the Stirling engine and heat pump.

Explanation of symbols

  24, 48: Heat exchange section, 25, 41: Ventilation path, 38a, 54a: Heat absorption head, 38b, 54b: Heat generation head, 100: Stirling engine, 148: Regenerator tube, 241: Hot air path section, 242: Wet Wind path section, 243: Circulation path section, 247: Warm air path section in water tank, 248: Humid air path section in water tank, 400, 500, 600, 700: Heating dehumidifier, 410, 510, 610, 710: Stirling engine 411, 511, 611, 711: heating head, 412, 512, 612, 712: heat absorption head, 420, 520, 620, 720: high temperature side heat exchange section, 421, 621: heating fin, 522, 722: heating section 430, 530, 630, 730: low temperature side heat exchange section, 532, 632: cooling section, 431, 731: cooling fins, 523, 53 , 633,723: the heat transfer medium flow path.

A heating and dehumidifying device according to one aspect of the present invention includes a first air passage for flowing gas, a second air passage, and a first air for heating gas flowing through the first air passage. A heat exchange section, a second heat exchange section for cooling the gas flowing through the second air passage, and a Stirling engine including a heat generating head and an endothermic head. It performs heat exchange to heat the gas in the heating head of the engine, the second heat exchanging part, the heat exchange line which have to cool the gas in heat absorption head of the Stirling engine, heating head, first It arrange | positions in an air path and comprises a 1st heat exchange part, and the 1st heat exchange part contains the fin arrange | positioned so that a heat generating head may be contacted .

In the heating and dehumidifying device according to one aspect of the present invention, the heat generating head is arranged in the first air passage and constitutes the first heat exchanging unit, whereby the heat generating head and the first heat exchanging unit are formed. A path for transferring heat to and from the unit becomes unnecessary, and wasteful consumption of heat in the path between the heat generating head and the first heat exchange unit can be prevented. In addition, the first heat exchanging unit includes fins arranged so as to be in contact with the heat generating head, whereby gas can be efficiently exchanged in the fins. In addition, the heat dehumidifying device can be reduced in size.

A heating and dehumidifying device according to another aspect of the present invention includes a first air passage for flowing a gas, a second air passage, and a first for heating the gas flowing through the first air passage. A heat exchange part, a second heat exchange part for cooling the gas flowing through the second air passage, and a Stirling engine including a heat generating head and an endothermic head, the first heat exchange part comprises: Heat exchange is performed so that gas is heated by the heat generating head of the Stirling engine, and the second heat exchanging unit performs heat exchange so that the gas is cooled by the heat absorbing head of the Stirling engine. It arrange | positions in a path | route and comprises a 2nd heat exchange part, and the 2nd heat exchange part contains the fin arrange | positioned so that a thermal absorption head may be contacted.

Conventionally, in a heat pump used in a heat dehumidifying apparatus, heat exchange is performed between a condensing unit that compresses a refrigerant by a compressor to change from gas to liquid and an evaporation unit that expands the refrigerant to change from liquid to gas. ing. That is, in the heat pump, the refrigerant moves from the condensing unit through the pipe or the like to the evaporating unit, changes from liquid to gas, and moves from the evaporating unit through the pipe or the like to the condensing unit to change from gas to liquid. It is necessary to repeat changing.
  On the other hand, the Stirling engine reciprocates the displacer in the cylinder, thereby compressing the working gas such as helium in the compression space to heat the heat generating head and expand the heat generating head to cool the heat absorbing head. As described above, in the Stirling engine, the working gas remains in a gaseous state and moves only between the compression space and the expansion space. The compression space and the expansion space are disposed at both ends of one cylinder, for example. In this case, the working gas reciprocates from one end of the cylinder to the other end while maintaining the gaseous state. .

As described above, in the Stirling engine, the moving distance of the working gas is short, and it is not necessary to change the state of the refrigerant between the gas and the liquid. Therefore, the responsiveness of the Stirling engine is higher than that of the heat pump. For example, the time required from the start of driving the Stirling engine until the heat generating head and the heat absorbing head reach a predetermined temperature, the evaporation unit and the condensing unit are set to a predetermined temperature after starting the heat pump. It is shorter than the time required to become.
  Therefore, by using a Stirling engine, it is not necessary to start up for a long time before the start of the drying operation or at the start of the drying operation. Therefore, the controllability is higher than that of the heat pump, and energy saving, that is, energy consumption is effectively reduced. Thus, it is possible to obtain a heating and dehumidifying device that facilitates energy saving. As described above, the heating and dehumidifying device including the Stirling engine can shorten the time required to start the heating and dehumidifying device, and is required when the operation is once interrupted and then restarted during the operation of the heating and dehumidifying device. Time can be shortened.

Further, the vibration system of the heat pump used in the conventional heat dehumidifying apparatus is a complicated vibration system including rotation vibration because a compressor is used for compression and expansion of the refrigerant. On the other hand, a Stirling engine has a simple vibration system compared to a heat pump. That is, in the Stirling engine, only a linear motion of reciprocation of the displacer is performed.
  Thus, since the Stirling engine has a simple vibration system, it is easy to absorb vibration. For example, the vibration can be easily suppressed by providing a vibration absorbing member such as a spring having the co-frequency of the displacer as the natural frequency. In a Stirling engine, vibration can be easily suppressed, so that noise due to vibration is less likely to occur.

  In this way, vibration and noise can be reduced, and usability, ie easy to use, energy saving, ie consumption, does not deteriorate the indoor environment where the dryer is installed. It is possible to provide a heating and dehumidifying device that can effectively reduce energy and facilitate energy saving.

In the heating and dehumidifying device according to another aspect of the present invention, the heat absorbing head is disposed in the second air passage and constitutes the second heat exchanging unit, whereby the heat absorbing head and the second heat A path for transmitting cold air to and from the exchange unit is not necessary, and it is possible to prevent wasteful consumption of cold air in the path between the heat absorbing head and the second heat exchange unit. Further, the second heat exchanging part includes the fins arranged so as to be in contact with the heat absorbing head, whereby the heat can be efficiently exchanged between the gases in the fins. In addition, the heat dehumidifying device can be reduced in size.

A heating and dehumidifying device according to one aspect of the present invention or another aspect includes an object container to be dried for accommodating an object to be dried and an object to rotate the object container to be dried. It is preferable to include a drying object storage container drive motor.

In the heating and dehumidifying apparatus according to one aspect of the present invention, the second heat exchanging unit has a cooling unit for cooling the gas and a heat conduction medium for conducting the heat of the heat absorbing head to the cooling unit. It is preferable to have a heat conducting medium flow path.

By doing in this way, it becomes easy to optimize the position and shape of a 2nd heat exchange part according to the shape of an air path, etc.

In the heating and dehumidifying device according to another aspect of the present invention, the first heat exchanging unit includes a heating unit for heating the gas and a heat conduction medium for conducting the heat of the heating head to the heating unit. It is preferable to have a heat conduction medium channel that circulates .

By doing in this way, it becomes easy to optimize the position and shape of a 1st heat exchange part according to the shape of an air path, etc.

A heating and dehumidifying device according to one aspect of the present invention or another aspect includes a circulation path for allowing gas to flow from the second air path into the first air path, The gas is preferably cooled in the second heat exchange section, flows into the first air path through the circulation path, and is heated in the first heat exchange section.

Thus, the gas that has flowed into the second air passage is cooled in the second heat exchange section, flows into the first air passage through the circulation path, and is heated in the first heat exchange section. Therefore, it can dehumidify efficiently.

A heating and dehumidifying device according to one aspect of the present invention or another aspect includes a connection pipe disposed between the heat generating head and the heat absorbing head, and the heat generating head is disposed in the first air passage. The first heat exchanging portion is configured, the heat absorbing head is disposed in the second air passage, and the second heat exchanging portion is configured, and the heat generating head, the heat absorbing head, and the connection pipe are coaxial. are arranged, the connecting pipe between the heating head and the heat absorption head is preferably Rukoto been placed in the circulation path.

Claims (9)

A first air passage and a second air passage for circulating gas;
A first heat exchange section for heating the gas flowing through the first air path;
A second heat exchange section for cooling the gas flowing through the second air passage;
A Stirling engine including a heat generating head and a heat absorbing head;
The first heat exchange unit performs heat exchange so as to heat the gas with the heat generating head of the Stirling engine,
The second heat exchanging unit is a heating and dehumidifying device that performs heat exchange so as to cool a gas with a heat absorbing head of the Stirling engine. A circulation path for allowing gas to flow from the second air path into the first air path;
The gas in the second air passage is cooled in the second heat exchange section, flows into the first air passage through the circulation path, and is heated in the first heat exchange section. The heat dehumidifying apparatus according to claim 1.   The heating and dehumidifying device according to claim 1 or 2, wherein the heat generating head is disposed in the first air passage to constitute the first heat exchange unit.   The heating and dehumidifying device according to claim 3, wherein the first heat exchange unit includes a fin disposed so as to be in contact with the heat generating head.   The first heat exchange unit includes a heating unit for heating a gas, and a heat conduction medium channel through which a heat conduction medium for conducting heat of the heat generating head to the heating unit flows. The heating and dehumidifying device according to any one of claims 1 to 4.   The heat dehumidifying device according to claim 1 or 2, wherein the heat absorbing head is disposed in the second air passage to constitute the second heat exchange unit.   The heating and dehumidifying device according to claim 6, wherein the second heat exchange unit includes a fin disposed so as to contact the heat absorbing head.   The second heat exchange unit includes a cooling unit for cooling a gas, and a heat conduction medium channel through which a heat conduction medium for conducting heat of the cooling head to the cooling unit flows. The heating and dehumidifying device according to any one of claims 1, 2, 6, and 7. A connecting pipe disposed between the heat generating head and the heat absorbing head;
The heat generating head is disposed in the first air passage to constitute the first heat exchange unit,
The heat absorbing head is disposed in the second air passage to constitute the second heat exchange unit,
The heat generating head, the heat absorbing head and the connecting pipe are arranged coaxially,
The heating and dehumidifying device according to claim 2, wherein the heat generating head, the heat absorbing head, and the connection pipe are disposed in the circulation path.

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